TW201346206A - Heat transfer pipe and heat exchanger using the same - Google Patents

Heat transfer pipe and heat exchanger using the same Download PDF

Info

Publication number
TW201346206A
TW201346206A TW102111910A TW102111910A TW201346206A TW 201346206 A TW201346206 A TW 201346206A TW 102111910 A TW102111910 A TW 102111910A TW 102111910 A TW102111910 A TW 102111910A TW 201346206 A TW201346206 A TW 201346206A
Authority
TW
Taiwan
Prior art keywords
tube
heat transfer
inner tube
support member
gap
Prior art date
Application number
TW102111910A
Other languages
Chinese (zh)
Inventor
Shigeaki Takinami
Shigetoshi Tanigawa
Original Assignee
Kasei Co C I
Cku Inc
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 Kasei Co C I, Cku Inc filed Critical Kasei Co C I
Publication of TW201346206A publication Critical patent/TW201346206A/en

Links

Classifications

    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/06—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with the heat-exchange conduits forming part of, or being attached to, the tank containing the body of fluid
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/02—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled
    • F28D7/026—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled the conduits of only one medium being helically coiled and formed by bent members, e.g. plates, the coils having a cylindrical configuration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/122—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and being formed of wires
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • F28F1/405—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element and being formed of wires
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/007—Auxiliary supports for elements
    • F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0229—Double end plates; Single end plates with hollow spaces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/04—Fastening; Joining by brazing

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

This invention provides a heat transfer pipe and a heat exchanger which assembles an outer pipe and an inner pipe with a high precision in a compact heat exchanger without causing decrease of heat transfer efficiency. The heat transfer pipe is characterized in including: a plurality of outer pipes (13); inner pipes (15) inserted in the outer pipes (13) and extending out of two ends; gap support members (17) disposed in the gap between inner peripheral surfaces of the outer pipes (13) and outer peripheral surfaces of the inner pipes (15) and including wire rods contacting the inner peripheral surfaces and the outer peripheral surfaces in spiral across almost whole length of the outer pipes (13); and support members (19) including wire rods contacting the inner peripheral surfaces of the inner pipe (15) in spiral across almost whole length of the inner pipes (15), and an area ratio between first channels in the inner pipes (15) and second channels of the out pipes (13) is 1: 1 to 1: 1.6.

Description

傳熱管及使用該傳熱管的熱交換器 Heat transfer tube and heat exchanger using the same

本發明涉及一種傳熱管及使用該傳熱管的多管式等熱交換器。 The present invention relates to a heat transfer tube and a multi-tube heat exchanger using the heat transfer tube.

作為多管式熱交換器，有如下的二重管(double pipe)式熱交換器，其將內管插通至外管內，且在內管內流通的流體和內管與外管之間流通的流體之間進行熱交換。該熱交換器適用於使用了冷媒的熱泵(heat pump)式熱水器或供暖設備等，在內管內流通高溫高壓的冷媒，並對內管與外管之間流通的水進行加熱而供給熱水。 As a multi-tube heat exchanger, there is a double pipe heat exchanger in which an inner tube is inserted into an outer tube, and a fluid flowing between the inner tube and the inner tube and the outer tube Heat exchange between the circulating fluids. The heat exchanger is applied to a heat pump type water heater or a heating device using a refrigerant, and a high temperature and high pressure refrigerant is passed through the inner tube, and water flowing between the inner tube and the outer tube is heated to supply hot water. .

在該二重管式熱交換器中，為了獲得規定的供給熱水能力，而增大傳熱面積並設為長條狀的二重管構成。因此，為了嵌入在設備內，必須進行彎折加工或盤繞而成形為規定的外形形狀，從而緊密化困難。此外，伴隨全長的長尺寸化，流體(冷媒、水)的壓力損失也會增大，因而必須使用大管徑的管體，從而無法使用相對於高壓冷媒而耐壓性優異的小徑管。針對所述課題，在下述專利文獻1中設為如下構成，即，將外管內插通著內管的二重管平行地並列配置多根，在該二重管的端部將內側集管(header pipe)接合而使外管連通，並將貫通了內側集管的內管與外側集管 接合而使其連通，從而使流體的壓力損失大幅地減少而可使用小徑管，可緊密地製作，且容易嵌入在設備內。 In the double tube heat exchanger, in order to obtain a predetermined hot water supply capability, a heat transfer area is increased and a double tube structure is formed. Therefore, in order to be embedded in the apparatus, it is necessary to perform bending or coiling to form a predetermined outer shape, which makes it difficult to close. In addition, as the length of the entire length increases, the pressure loss of the fluid (refrigerant or water) increases. Therefore, it is necessary to use a large-diameter pipe body, and it is not possible to use a small-diameter pipe excellent in pressure resistance with respect to the high-pressure refrigerant. In the following Patent Document 1, the following Patent Document 1 has a configuration in which a plurality of double tubes in which an outer tube is inserted through an inner tube are arranged in parallel, and an inner tube is disposed at an end portion of the double tube. The header pipe is joined to connect the outer tube, and the inner tube and the outer tube that penetrate the inner header By joining and connecting them, the pressure loss of the fluid is greatly reduced, and a small diameter pipe can be used, which can be closely produced and easily embedded in the apparatus.

現有技術文獻 Prior art literature 專利文獻 Patent literature

專利文獻1：日本專利特開2005-127684號公報 Patent Document 1: Japanese Patent Laid-Open Publication No. 2005-127684

然而，所述現有的二重管式熱交換器為了實現緊密化而使用內管及外管的直徑小的管，但必須構成為使流體確實地通過外管與內管的間隙部分以進行傳熱，對於這些外管與內管及集管的接合部分的製作而言要求精度。一般來說，是利用焊接來進行所述管體的接合，焊料會因接合時的加熱而溢出並流動，從而可看到向外部流出的焊料，但因為是二重管構造，所以在管內部流動的情況下無法看到，如果浸入內管與外管的間隙部分等則會妨礙流路，也就是流路剖面積並不固定，從而有時無法獲得充分的傳熱效率。 However, the conventional double-tube heat exchanger uses a tube having a small diameter of the inner tube and the outer tube in order to achieve compaction, but must be configured such that the fluid surely passes through the gap portion between the outer tube and the inner tube for transmission. Heat requires precision for the production of the joint between the outer tube and the inner tube and the header. In general, the joining of the pipe body is performed by welding, and the solder overflows and flows due to heating at the time of joining, so that the solder flowing out to the outside can be seen, but since it is a double pipe structure, it is inside the pipe. When the flow is not observed, if the gap between the inner tube and the outer tube is immersed, the flow path is hindered, that is, the cross-sectional area of the flow path is not fixed, and sufficient heat transfer efficiency may not be obtained.

此外，專利文獻1的二重管式熱交換器的內管的中心呈一條直線地形成空間，熱媒流的阻力雖小，但未與內管接觸而流動的熱媒量多，從而存在無法有效地進行熱交換的問題。 Further, in the double tube heat exchanger of Patent Document 1, the center of the inner tube is formed in a straight line, and the resistance of the heat medium flow is small, but the amount of heat medium that does not flow in contact with the inner tube is large, and thus it is impossible to The problem of efficient heat exchange.

本發明鑒於所述狀況而完成，其目的在於提供一種傳熱管及使用該傳熱管的熱交換器，所述傳熱管在緊密的熱交換器中高精度地組裝外管與內管，不會引起傳熱效率的降低，並且可提高內管與該內管中流動的熱媒的熱交換效率。 The present invention has been made in view of the above circumstances, and an object thereof is to provide a heat transfer tube that heats an outer tube and an inner tube with high precision in a compact heat exchanger, and a heat exchanger using the heat transfer tube This causes a decrease in heat transfer efficiency and improves the heat exchange efficiency of the inner tube and the heat medium flowing in the inner tube.

接著，參照與實施方式相對應的附圖來對用以解決所述課題的 手段進行說明。 Next, with reference to the drawings corresponding to the embodiments, the problem for solving the problem is solved. Means to explain.

本發明的技術方案1所述的傳熱管11的特徵在於包括：外管13；內管15，***至所述外管13；間隙支撐構件17，配置在所述外管13的內周面與所述內管15的外周面的間隙長度(間隙幅長)W內，且包含遍及所述外管13的大致全長而螺旋狀地與所述內周面及外周面接觸的線材；以及支撐構件19，包含遍及該內管15的全長而螺旋狀地與所述內管15的內周面接觸的線材。 The heat transfer tube 11 according to the first aspect of the present invention includes: an outer tube 13; an inner tube 15 inserted into the outer tube 13; and a gap supporting member 17 disposed on an inner circumferential surface of the outer tube 13 a wire having a gap length (gap length) W with respect to an outer circumferential surface of the inner tube 15, and a wire material that is spirally connected to the inner circumferential surface and the outer circumferential surface over substantially the entire length of the outer tube 13; The member 19 includes a wire member that spirally contacts the inner circumferential surface of the inner tube 15 over the entire length of the inner tube 15.

該傳熱管11成為支撐構件19從內側對作為一次流路的內管15進行支撐的結構，並且內管15與外管13由間隙支撐構件17來支撐，該間隙支撐構件17使作為剖面環狀的管狀間隙的二次流路遍及周向(circumferential direction)而成為相等的間隙來進行定位，從而外管13與內管15組裝時彼此的配置精度提高，且實現組裝步驟的簡化。此外，不會在外管13與內管15的配置位置發生偏離，流路剖面積固定，從而傳熱效率不會降低。 The heat transfer tube 11 has a structure in which the support member 19 supports the inner tube 15 as a primary flow path from the inside, and the inner tube 15 and the outer tube 13 are supported by the gap support member 17, which serves as a section ring The secondary flow path of the tubular gap is positioned in the circumferential direction and becomes an equal gap, so that the arrangement accuracy of the outer tube 13 and the inner tube 15 is improved, and the assembly procedure is simplified. Further, the position of the outer tube 13 and the inner tube 15 is not deviated, and the cross-sectional area of the flow path is fixed, so that the heat transfer efficiency is not lowered.

技術方案2所述的傳熱管11的特徵在於：在技術方案1所述的傳熱管11中，所述間隙支撐構件17包含捲材，線徑d1設為與所述間隙長度(間隙幅長)W大致相等。 The heat transfer tube 11 according to claim 2 is characterized in that in the heat transfer tube 11 according to the first aspect, the gap support member 17 includes a coil, and the wire diameter d1 is set to be the gap length (gap width) Long) W is roughly equal.

該傳熱管11中，可利用包含捲材的間隙支撐構件17，而容易地將外管13與內管15的間隙保持為固定來進行組裝，且以固定的間隙來確保流路。此外，也為了傳熱而***間隙支撐構件17，從而傳熱面積設定得大。 In the heat transfer tube 11, the gap support member 17 including the coil material can be used, and the gap between the outer tube 13 and the inner tube 15 can be easily fixed and assembled, and the flow path can be secured with a fixed gap. Further, the gap supporting member 17 is also inserted for heat transfer, so that the heat transfer area is set large.

技術方案3所述的傳熱管11的特徵在於：在技術方案1所述的 傳熱管11中，所述間隙支撐構件45包含小徑部43與大徑部41交替地形成的捲材，線徑d1比所述間隙長度(間隙幅長)W小，所述小徑部43的捲內徑D1設為所述內管15的外徑D5，所述大徑部41的捲外徑D2設為所述外管13的內徑D4，且所述內管15支撐於所述外管13內。 The heat transfer tube 11 according to claim 3 is characterized in that: In the heat transfer tube 11, the gap support member 45 includes a coil material in which the small diameter portion 43 and the large diameter portion 41 are alternately formed, and the wire diameter d1 is smaller than the gap length (gap length) W, and the small diameter portion is small. The inner diameter D1 of the inner tube 15 is set to the outer diameter D5 of the inner tube 15, the outer diameter D2 of the large diameter portion 41 is set to the inner diameter D4 of the outer tube 13, and the inner tube 15 is supported by the inner tube 15. Said inside the outer tube 13.

該傳熱管11中，間隙支撐構件45的小徑部43對內管15進行支撐，大徑部41由外管13的內周面支撐，在內管15的外周面與外管13的內周面的間隙長度(間隙幅長)W***間隙支撐構件45的線徑d1與空隙47，因而可充分地確保流路面積。 In the heat transfer tube 11, the small diameter portion 43 of the gap support member 45 supports the inner tube 15, and the large diameter portion 41 is supported by the inner peripheral surface of the outer tube 13, and the outer peripheral surface of the inner tube 15 and the outer tube 13 are inside. The gap length (gap length) of the circumferential surface is inserted into the wire diameter d1 of the gap support member 45 and the gap 47, so that the flow path area can be sufficiently ensured.

技術方案4所述的傳熱管11的特徵在於包括：外管13；內管15，***至所述外管13；間隙支撐構件17，配置在外管內周面32與內管外周面30的間隙31內，且包含遍及所述外管13的大致全長而螺旋狀地與所述外管內周面32及所述內管外周面30接觸的線材；支撐構件19，包含遍及所述內管15的全長而螺旋狀地與所述內管內周面38接觸的線材；以及傳熱構件20，遍及所述支撐構件19的全長設置在所述支撐構件19的中心，且至少外周的一部分與所述支撐構件19接觸。 The heat transfer tube 11 according to claim 4 is characterized by comprising: an outer tube 13; an inner tube 15 inserted into the outer tube 13; and a gap supporting member 17 disposed on the inner peripheral surface 32 of the outer tube and the outer peripheral surface 30 of the inner tube In the gap 31, a wire member that spirally contacts the outer tube inner peripheral surface 32 and the inner tube outer peripheral surface 30 over substantially the entire length of the outer tube 13 is included; the support member 19 includes the inner tube a wire member having a full length and spirally contacting the inner circumferential surface 38 of the inner tube; and a heat transfer member 20 disposed at a center of the support member 19 over the entire length of the support member 19, and at least a part of the outer circumference The support member 19 is in contact.

在該傳熱管11中，內管15中流動的熱媒一邊與設置於內管15的內側的傳熱構件20接觸且與支撐構件19接觸一邊流動，由此對在內管15內的熱媒施加流動阻力，而形成如蜿蜒般的流動，以前，為只有在內管15內筆直地流動且與內管內周面38鄰接的熱媒對內管15進行熱交換的狀態，由此熱媒的接觸面積增大。熱媒通過與傳熱構件20進行接觸，而與該傳熱構件20、支撐構件19及內管內周面38進行接觸，對這些傳熱構件20、 支撐構件19、內管15傳遞熱，從而進行熱交換。經熱交換的熱量通過熱傳導而傳遞至內管外周面30，與在外管13和內管15的間隙31內流動的另一系統的熱媒進行熱交換。也就是，與傳熱構件20交換的熱量有助於重新提高熱交換效率。 In the heat transfer tube 11, the heat medium flowing in the inner tube 15 flows while being in contact with the heat transfer member 20 provided inside the inner tube 15 and in contact with the support member 19, thereby heating the inner tube 15 The medium exerts a flow resistance to form a flow like a crucible. In the past, a state in which only the heat medium flowing in the inner tube 15 and flowing adjacent to the inner peripheral surface 38 of the inner tube exchanges heat with the inner tube 15 is performed. The contact area of the heat medium is increased. The heat medium comes into contact with the heat transfer member 20, and comes into contact with the heat transfer member 20, the support member 19, and the inner tube inner peripheral surface 38, and the heat transfer member 20, The support member 19 and the inner tube 15 transfer heat to perform heat exchange. The heat exchanged heat is transferred to the inner peripheral surface 30 of the inner tube by heat conduction, and exchanges heat with the heat medium of another system flowing in the gap 31 between the outer tube 13 and the inner tube 15. That is, the heat exchanged with the heat transfer member 20 contributes to a renewed heat exchange efficiency.

本發明的技術方案5所述的傳熱管11的特徵在於：其為技術方案4所述的傳熱管11，所述傳熱構件20為在所述支撐構件19的長度方向上是長的且螺旋狀地扭轉的帶板141。 The heat transfer tube 11 according to claim 5 of the present invention is characterized in that it is the heat transfer tube 11 according to claim 4, and the heat transfer member 20 is long in the longitudinal direction of the support member 19. And a strip 141 that is twisted in a spiral shape.

在該傳熱管11中，帶板141一邊與支撐構件19接觸一邊螺旋狀地設置，在內管15內流動的熱媒一邊螺旋旋轉一邊在內管15中前進。由此，相比於熱媒與軸線平行地流動的情況，可增大熱媒與傳熱構件20接觸的接觸面積及接觸時間。 In the heat transfer tube 11, the strip plate 141 is spirally provided while being in contact with the support member 19, and the heat medium flowing in the inner tube 15 advances in the inner tube 15 while spirally rotating. Thereby, the contact area and contact time of the contact of the heat medium with the heat transfer member 20 can be increased as compared with the case where the heat medium flows in parallel with the axis.

本發明的技術方案6所述的傳熱管11的特徵在於：其為技術方案4所述的傳熱管11，所述傳熱構件20為外周部凸出圓桿153，該外周部凸出圓桿153具有在所述支撐構件19的長度方向上每隔規定間隔擠壓圓形外周而變形的長圓部155。 The heat transfer tube 11 according to the sixth aspect of the present invention is characterized in that it is the heat transfer tube 11 according to claim 4, and the heat transfer member 20 is a peripheral portion projecting round rod 153, and the outer peripheral portion is convex. The round rod 153 has an oblong portion 155 which is deformed by pressing a circular outer circumference at regular intervals in the longitudinal direction of the support member 19.

在該傳熱管11中，圓桿原材料以從軸線正交方向夾持的方式而被擠壓，由此被擠壓的部分向半徑方向外側凸出，從而成為長圓部155。該長圓部155的凸出前端側與支撐構件19接觸。通過使該擠壓方向例如每90度地交替地改變，而可對熱媒的流路進行攪拌且使其蜿蜒。 In the heat transfer tube 11, the round rod material is pressed so as to be sandwiched in the direction orthogonal to the axis, whereby the pressed portion protrudes outward in the radial direction to form the oblong portion 155. The convex front end side of the oblong portion 155 is in contact with the support member 19. By alternately changing the pressing direction, for example, every 90 degrees, the flow path of the heat medium can be stirred and twisted.

本發明的技術方案7所述的傳熱管11的特徵在於：其為技術方案4所述的傳熱管11，所述傳熱構件20為異徑圓桿161，該異徑圓桿161是在所述支撐構件19的長度方向上每隔規定間隔使圓形外周由小徑部159與大徑部157交替形成。 The heat transfer tube 11 according to the seventh aspect of the present invention is characterized in that it is the heat transfer tube 11 according to claim 4, and the heat transfer member 20 is a reducer round rod 161, and the reducer round rod 161 is The circular outer circumference is alternately formed by the small diameter portion 159 and the large diameter portion 157 at predetermined intervals in the longitudinal direction of the support member 19.

在該傳熱管11中，通過將異徑圓桿161***至內管15，沿著異 徑圓桿161流動的熱媒一邊與大徑部157碰撞一邊流動。由該碰撞而打亂熱媒的流動，在不與內管內周面38或傳熱構件20接觸的狀態下直接通過的熱媒得以減少。 In the heat transfer tube 11, by inserting the different diameter round rod 161 into the inner tube 15, The heat medium flowing through the radial rod 161 flows while colliding with the large diameter portion 157. The flow of the heat medium is disturbed by the collision, and the heat medium that passes directly without being in contact with the inner tube inner peripheral surface 38 or the heat transfer member 20 is reduced.

本發明的技術方案8所述的傳熱管11的特徵在於：其為技術方案4所述的傳熱管11，所述傳熱構件20為剖面是多邊形狀的實心桿165。 The heat transfer tube 11 according to the eighth aspect of the present invention is characterized in that it is the heat transfer tube 11 according to the fourth aspect, and the heat transfer member 20 is a solid rod 165 having a polygonal cross section.

在該傳熱管11中，相比於主要僅表背面與熱媒接觸的帶板141，例如通過剖面是三角形狀的傳熱構件20，而可使與熱媒的接觸位置為多個部位。尤其是如果將剖面形狀設為星形等則不會減少流路，而可進一步增大接觸面積。 In the heat transfer tube 11, the contact plate with the heat medium can be made into a plurality of portions, for example, by the heat transfer member 20 having a triangular cross section, for example, only the heat transfer member 20 having a triangular cross section in contact with the heat medium. In particular, if the cross-sectional shape is set to a star shape or the like, the flow path is not reduced, and the contact area can be further increased.

本發明的技術方案9所述的熱交換器49的特徵在於：使用了技術方案1至技術方案8中任一項所述的傳熱管11，所述傳熱管11相互平行而配置著多個，將所有內管入口端連接於一次分支管21且將所有內管出口端連接於一次集合管27而構成一次流路，並且將所有外管入口端連接於二次分支管25且將所有外管出口端連接於二次集合管29而構成二次流路。 The heat exchanger 49 according to claim 9 of the present invention is characterized in that the heat transfer tubes 11 according to any one of the first to eighth aspects are used, and the heat transfer tubes 11 are arranged in parallel with each other. Connect all the inner tube inlet ends to the primary branch tube 21 and connect all the inner tube outlet ends to the primary manifold 27 to form a primary flow path, and connect all outer tube inlet ends to the secondary branch tube 25 and all The outlet end of the outer tube is connected to the secondary collecting pipe 29 to constitute a secondary flow path.

在該熱交換器49中，由多個傳熱管11相互平行地構成，於同一平面上鄰接地排列著，且配置著外管13及內管15。此外，可將在該平面上構成的熱交換器49設為1個單元，且積層多段而構成，從而可構成擴大了傳熱面積且接地面積小的熱交換器。 In the heat exchanger (49), the plurality of heat transfer tubes (11) are formed in parallel with each other, and are arranged adjacent to each other on the same plane, and the outer tube (13) and the inner tube (15) are disposed. In addition, the heat exchanger 49 formed on the flat surface can be configured as a single unit, and a plurality of layers can be stacked to form a heat exchanger having a large heat transfer area and a small ground contact area.

此外，在包括傳熱構件20的熱交換器49中，內管15中流動的熱媒一邊與設置在內管15的內側的傳熱構件20接觸一邊流動，以前僅與內管內周面38接觸的熱媒的接觸面積增大。熱媒通過與傳熱構件20接觸而利用熱傳遞與傳熱構件20進行熱交換。經熱交換的熱量利用熱傳導而傳 遞至內管15，且與在外管13和內管15的間隙31內流動的另一系統的熱媒進行熱交換。也就是，與傳熱構件20交換的熱量有助於重新提高熱交換效率。此外，該熱交換器49中，由包含外管13及內管15的多個傳熱管11相互平行地構成，且在同一平面上鄰接地排列著。在該平面上構成的熱交換器49可設為一個單元，且積層多段而構成，從而可在擴大傳熱面積的同時減小接地面積而構成。 Further, in the heat exchanger 49 including the heat transfer member 20, the heat medium flowing in the inner tube 15 flows while being in contact with the heat transfer member 20 provided inside the inner tube 15, and previously only the inner peripheral surface 38 of the inner tube The contact area of the contacted heat medium is increased. The heat medium exchanges heat with the heat transfer member 20 by heat transfer by coming into contact with the heat transfer member 20. Heat exchanged by heat is transmitted by heat conduction It is delivered to the inner tube 15 and exchanges heat with another system of heat medium flowing in the gap 31 between the outer tube 13 and the inner tube 15. That is, the heat exchanged with the heat transfer member 20 contributes to a renewed heat exchange efficiency. Further, in the heat exchanger (49), the plurality of heat transfer tubes (11) including the outer tube (13) and the inner tube (15) are formed in parallel with each other, and are arranged adjacent to each other on the same plane. The heat exchanger 49 formed on this plane can be configured as one unit and laminated in a plurality of stages, so that the heat transfer area can be enlarged and the ground contact area can be reduced.

技術方案10所述的熱交換器65的特徵在於：使用了技術方案1至技術方案8中任一項所述的傳熱管11，將多根所述傳熱管11予以成束，將該傳熱管11的束收容在圓筒形狀的殼體67內，將所述內管15的入口端彼此及出口端彼此分別連接而構成一次流路，並且將所述外管13的入口端彼此及出口端彼此分別連接而構成二次流路，且在所述殼體67內作為三次流路而構成。 The heat exchanger 65 according to claim 10 is characterized in that the heat transfer tubes 11 according to any one of claims 1 to 8 are used, and a plurality of the heat transfer tubes 11 are bundled. The bundle of the heat transfer tubes 11 is housed in a cylindrical casing 67, and the inlet ends of the inner tubes 15 and the outlet ends are connected to each other to constitute a primary flow path, and the inlet ends of the outer tubes 13 are mutually connected. The outlet ends are connected to each other to form a secondary flow path, and are configured as a tertiary flow path in the casing 67.

在該熱交換器65中，成束的多個傳熱管11利用各個外管13與內管15而在圓筒形殼體67內進行熱交換，並且也可與在殼體67內流動的熱媒進行熱交換。 In the heat exchanger (65), the bundled plurality of heat transfer tubes (11) are heat-exchanged in the cylindrical casing (67) by the respective outer tubes (13) and the inner tubes (15), and may also flow in the casing (67). The heat medium performs heat exchange.

技術方案11所述的熱交換器65的特徵在於：在技術方案10所述的熱交換器65中，在所述殼體67內設置著多個整流板87，所述整流板87具有與所述傳熱管11的長度方向正交的面，對各所述傳熱管11進行支撐並且使所述三次流路蜿蜒。 The heat exchanger 65 according to claim 11 is characterized in that in the heat exchanger (65) according to the tenth aspect, a plurality of rectifying plates (87) are provided in the casing (67), and the rectifying plate (87) has a The heat transfer tubes 11 are supported on the surfaces of the heat transfer tubes 11 in the longitudinal direction, and the third flow paths are supported.

在該熱交換器65中，殼體67內流動的熱媒利用整流板87而蜿蜒，一邊使三次流路形成得長，一邊相對於殼體67內的各傳熱管11而在與長度方向大致正交的方向上流動，且熱媒利用各傳熱管11的外管13增大傳熱面積而進行熱交換。 In the heat exchanger (65), the heat medium flowing in the casing (67) is twisted by the rectifying plate (87), and the length of the third flow path is formed long with respect to each of the heat transfer tubes (11) in the casing (67). The direction flows in a direction substantially orthogonal to each other, and the heat medium exchanges heat with the outer tube 13 of each heat transfer tube 11 to exchange heat.

根據本發明的技術方案1所述的傳熱管，內管與外管由間隙支 撐構件而支撐，該間隙支撐構件使作為剖面環狀的管狀間隙的二次流路遍及周向而成為相等的間隙來進行定位，從而外管與內管組裝時彼此的配置精度提高，且實現組裝步驟的簡化。此外，通過具有間隙支撐構件及支撐構件，而內管與外管的位置不會發生偏移，在相互焊接等時焊料不會偏離或溢出，從而可分別固定位置。此外，間隙支撐構件及支撐構件成為支撐內管壁及外管壁的結構，由此可使這些內管及外管的壁厚薄型化，從而導熱率可進一步提高，也可進一步實現熱交換器的緊密化。此外，不會在外管與內管的配置位置發生偏離而同軸心地進行定位，流路剖面積固定且傳熱效率不會降低。此外，因流路形成為螺旋狀所以在管軸方向上管內的流體順暢地流動，並均勻地傳熱至整個管壁，而且間隙支撐構件與支撐構件成為傳熱體，從而可提高傳熱效率。 According to the heat transfer tube of claim 1 of the present invention, the inner tube and the outer tube are supported by the gap Supported by a support member that positions the secondary flow path of the tubular gap having a circular cross section in the circumferential direction and becomes an equal gap, thereby improving the arrangement accuracy of the outer tube and the inner tube when assembled, and realizing Simplification of the assembly steps. Further, by having the gap supporting member and the supporting member, the positions of the inner tube and the outer tube are not displaced, and the solder does not deviate or overflow when soldering or the like, and the positions can be fixed. Further, since the gap supporting member and the supporting member are configured to support the inner tube wall and the outer tube wall, the thickness of the inner tube and the outer tube can be made thinner, so that the thermal conductivity can be further improved, and the heat exchanger can be further realized. Closer. Further, the positioning of the outer tube and the inner tube does not deviate and the positioning is performed concentrically, the flow path sectional area is fixed, and the heat transfer efficiency is not lowered. Further, since the flow path is formed in a spiral shape, the fluid in the tube flows smoothly in the tube axis direction, and heat is uniformly transferred to the entire tube wall, and the gap support member and the support member become heat transfer bodies, thereby improving heat transfer. effectiveness.

根據技術方案2所述的傳熱管由包含捲材的間隙支撐構件構成，由此可容易地將外管與內管的間隙保持為固定來進行組裝，也就是，在相互***、嵌合時間隙支撐構件成為導件(guide)，可進行組裝的容易度與精度高的安裝，且能夠以固定的間隙確保流路。 According to the heat transfer tube of the second aspect, the heat transfer tube is composed of a gap supporting member including a coil, whereby the gap between the outer tube and the inner tube can be easily fixed and assembled, that is, at the time of mutual insertion and fitting. The gap support member serves as a guide, and can be easily assembled and mounted with high precision, and the flow path can be secured with a fixed gap.

根據技術方案3所述的傳熱管，間隙支撐構件的小徑部對內管進行支撐，大徑部由外管的內周面支撐，在內管的外周面與外管的內周面的間隙部分***間隙支撐構件的線徑及空隙，因而可充分地確保流路面積。 According to the heat transfer tube of claim 3, the small diameter portion of the gap support member supports the inner tube, and the large diameter portion is supported by the inner peripheral surface of the outer tube, and the outer peripheral surface of the inner tube and the inner peripheral surface of the outer tube The gap portion is inserted into the wire diameter and the gap of the gap supporting member, so that the flow path area can be sufficiently ensured.

此外，根據本發明的技術方案4所述的傳熱管，內管與外管由間隙支撐構件而支撐，該間隙支撐構件使作為剖面環狀的管狀間隙的二次流路遍及周向而成為相等的間隙來進行定位，從而外管與內管組裝時彼此的配置精度提高，且實現組裝步驟的簡化。此外，通過具有間隙支撐構件及支撐構件，而內管與外管的位置不會發生偏移，在相互焊接等時焊料不會偏離或溢出，從而可分別固定位置。此外，間隙支撐構件及支撐構件成 為支撐內管壁及外管壁的結構，由此可將這些內管及外管的壁厚薄型化，從而導熱率可進一步提高，也可進一步實現熱交換器的緊密化。此外，傳熱構件支撐著支撐構件，可使支撐構件與內管密接。此外，不會在外管與內管的配置位置發生偏離而同軸心地進行定位，流路剖面積固定且傳熱效率不會降低。此外，利用間隙支撐構件與支撐構件而使流路形成為螺旋狀，且利用傳熱構件以蜿蜒的方式進行流動，因而朝向管軸方向的管內的流體充分地進行接觸而流動，從而可均勻地傳熱至整個管壁，且間隙支撐構件、支撐構件、傳熱構件分別為傳熱體，從而可提高傳熱效率。 Further, according to the heat transfer tube according to claim 4 of the present invention, the inner tube and the outer tube are supported by the gap supporting member, and the gap supporting member makes the secondary flow path of the tubular gap which is a cross section annular in the circumferential direction Equal gaps are used for positioning, so that the arrangement accuracy of each other when the outer tube and the inner tube are assembled is improved, and the assembly step is simplified. Further, by having the gap supporting member and the supporting member, the positions of the inner tube and the outer tube are not displaced, and the solder does not deviate or overflow when soldering or the like, and the positions can be fixed. In addition, the gap support member and the support member are formed In order to support the structure of the inner tube wall and the outer tube wall, the thickness of the inner tube and the outer tube can be made thinner, so that the thermal conductivity can be further improved, and the heat exchanger can be further compacted. Further, the heat transfer member supports the support member to allow the support member to be in close contact with the inner tube. Further, the positioning of the outer tube and the inner tube does not deviate and the positioning is performed concentrically, the flow path sectional area is fixed, and the heat transfer efficiency is not lowered. Further, the flow path is formed in a spiral shape by the gap support member and the support member, and the heat transfer member flows in a meandering manner, so that the fluid in the tube in the tube axis direction is sufficiently brought into contact and flows. The heat is uniformly transferred to the entire pipe wall, and the gap supporting member, the supporting member, and the heat transfer member are respectively heat transfer bodies, so that heat transfer efficiency can be improved.

根據技術方案5所述的傳熱管，因為是廉價的材料，所以不會相對地增大流動損失，利用呈螺旋狀扭轉的帶板而使內管內的熱媒螺旋旋轉，由此可提高內管與該內管中流動的熱媒的熱交換率。 According to the heat transfer tube of the fifth aspect, since the heat transfer tube is an inexpensive material, the flow loss is not relatively increased, and the heat medium in the inner tube is spirally rotated by the spirally twisted strip. The heat exchange rate between the inner tube and the heat medium flowing in the inner tube.

根據技術方案6所述的傳熱管，朝向半徑方向外側凸出的長圓部的凸出前端側與支撐構件進行接觸，該長圓部可對熱媒的流路進行攪拌而使其蜿蜒，由此可提高內管內流動的熱媒的熱交換率。 According to the heat transfer tube according to the sixth aspect of the invention, the projecting distal end side of the oblong portion that protrudes outward in the radial direction is in contact with the support member, and the oblong portion can agitate and smash the flow path of the heat medium. This can increase the heat exchange rate of the heat medium flowing in the inner tube.

根據技術方案7所述的傳熱管，利用異徑圓桿的大徑部與小徑部來對內管中流動的熱媒進行攪拌，而可容易與內管及傳熱構件接觸，從而熱交換率提高。 According to the heat transfer tube according to the seventh aspect of the invention, the large-diameter portion and the small-diameter portion of the reducer rod are used to agitate the heat medium flowing in the inner tube, so that the inner tube and the heat transfer member can be easily brought into contact with each other. The exchange rate is increased.

根據技術方案8所述的傳熱管，可增大傳熱構件的表面積，且可提高熱媒與傳熱構件及支撐構件的熱交換率。 According to the heat transfer tube of claim 8, the surface area of the heat transfer member can be increased, and the heat exchange rate between the heat medium and the heat transfer member and the support member can be improved.

根據本發明的技術方案9所述的熱交換器，將長度固定的多個傳熱管在同一平面上排列，可在有限的設置面積內擴大一次熱媒與二次熱媒的傳熱面積，從而可獲得溫度效率高的節省空間的熱交換器。此外，可將該平面狀的熱交換器作為單元積層多段而構成，提高內管與該內管中流動的熱媒的熱交換效率，從而可構成以小的設置面積緊密地構成的高效率 的熱交換器。 According to the heat exchanger of the ninth aspect of the present invention, the plurality of heat transfer tubes having a fixed length are arranged on the same plane, and the heat transfer area of the primary heat medium and the secondary heat medium can be expanded within a limited installation area. Thereby, a space-efficient heat exchanger with high temperature efficiency can be obtained. Further, the planar heat exchanger can be configured as a plurality of unit layers, and the heat exchange efficiency between the inner tube and the heat medium flowing through the inner tube can be improved, and a high efficiency which is closely configured with a small installation area can be formed. Heat exchanger.

根據技術方案10所述的熱交換器，可利用間隙支撐構件或支撐構件而高精度地構成內管及外管的相互的配置位置，即便分別成束而構成，一次流路與二次流路也不會不均勻，多個傳熱管成為束而構成且配置在圓筒形殼體內，從而可在內管、外管、殼體中由3種熱媒來確實地進行熱交換。 According to the heat exchanger of the tenth aspect, the gap between the inner tube and the outer tube can be accurately formed by the gap support member or the support member, and the first and second flow paths can be configured even if they are bundled separately. Further, the plurality of heat transfer tubes are formed in a bundle and are disposed in the cylindrical casing, so that heat exchange can be surely performed by the three types of heat medium in the inner tube, the outer tube, and the casing.

根據技術方案11所述的熱交換器，可利用設置在殼體內的整流板而使在殼體內流動的熱媒蜿蜒，從而可增大相對於傳熱管的傳熱面積。 According to the heat exchanger of the eleventh aspect, the heat medium flowing in the casing can be made by the rectifying plate provided in the casing, so that the heat transfer area with respect to the heat transfer pipe can be increased.

11‧‧‧傳熱管 11‧‧‧ heat transfer tube

13‧‧‧外管 13‧‧‧External management

15‧‧‧內管 15‧‧‧Inside

17、45‧‧‧間隙支撐構件 17, 45‧‧‧ clearance support members

19‧‧‧支撐構件 19‧‧‧Support members

20‧‧‧傳熱構件 20‧‧‧ Heat transfer components

21‧‧‧一次分支管 21‧‧‧A branch pipe

23‧‧‧栓塞 23‧‧ ‧ embolization

25‧‧‧二次分支管 25‧‧‧Second branch

27‧‧‧一次集合管 27‧‧‧One collection tube

29‧‧‧二次集合管 29‧‧‧Second collection tube

30‧‧‧內管外周面 30‧‧‧ inner tube outer circumference

31‧‧‧間隙 31‧‧‧ gap

32‧‧‧外管內周面 32‧‧‧The inner circumference of the outer tube

33‧‧‧外管***孔 33‧‧‧Outer tube insertion hole

35‧‧‧內管貫通孔 35‧‧‧Inner pipe through hole

37‧‧‧內管***孔 37‧‧‧Inner tube insertion hole

38‧‧‧內管內周面 38‧‧‧ inner tube inner circumference

39‧‧‧傳熱管列單元 39‧‧‧Heat transfer tube unit

41、157‧‧‧大徑部 41, 157‧‧‧ Large Path Department

43、159‧‧‧小徑部 43, 159‧‧‧ Small Trails Department

47‧‧‧空隙 47‧‧‧ gap

49、65‧‧‧熱交換器 49, 65‧‧ ‧ heat exchanger

51‧‧‧一次入口集管 51‧‧‧One entry manifold

53‧‧‧一次出口集管 53‧‧‧One export header

55‧‧‧二次入口集管 55‧‧‧Secondary inlet header

57‧‧‧二次出口集管 57‧‧‧Secondary export header

59‧‧‧旋入式管接頭 59‧‧‧ Screw-in fittings

61‧‧‧底板 61‧‧‧floor

67‧‧‧殼體 67‧‧‧Shell

69‧‧‧一次隔離壁 69‧‧‧ a partition wall

71‧‧‧內管支撐孔(一次支撐孔) 71‧‧‧Inner tube support hole (primary support hole)

73‧‧‧二次隔離壁 73‧‧‧Secondary partition

75‧‧‧外管支撐孔(二次支撐孔) 75‧‧‧Outer tube support hole (secondary support hole)

77‧‧‧端部壁 77‧‧‧End wall

79‧‧‧一次分支部 79‧‧‧One branch

81‧‧‧一次集合部 81‧‧‧One collection department

83‧‧‧二次分支部 83‧‧‧Second branch

85‧‧‧二次集合部 85‧‧‧Second Collection Department

87‧‧‧整流板 87‧‧‧Rectifier board

89‧‧‧通過部 89‧‧‧Driving Department

91‧‧‧一次入口集管 91‧‧‧One entry manifold

93‧‧‧二次出口集管 93‧‧‧Secondary export header

95‧‧‧三次入口集管 95‧‧‧Three inlet headers

97‧‧‧一次出口集管 97‧‧‧One export header

99‧‧‧二次入口集管 99‧‧‧Secondary inlet manifold

101‧‧‧三次出口集管 101‧‧‧ three export headers

141‧‧‧帶板 141‧‧‧With board

151‧‧‧切口 151‧‧‧ incision

153‧‧‧外周部凸出圓桿 153‧‧‧The outer perimeter protrudes from the round rod

155‧‧‧長圓部 155‧‧‧The long round

161‧‧‧異徑圓桿 161‧‧‧Reducing round rod

163‧‧‧圓桿 163‧‧‧ round rod

165‧‧‧實心桿 165‧‧‧solid rod

d1、d2‧‧‧線徑 D1, d2‧‧‧ wire diameter

D1‧‧‧捲內徑 D1‧‧‧ roll inner diameter

D2、D3‧‧‧捲外徑 D2, D3‧‧ vol.

D4、D6、D7‧‧‧內徑 D4, D6, D7‧‧‧ inner diameter

D5‧‧‧外徑 D5‧‧‧ OD

S1‧‧‧一次流路的面積 S1‧‧‧ area of a flow path

S2‧‧‧二次流路的面積 S2‧‧‧ area of secondary flow path

圖1(a)是表示本發明的傳熱管的示意放大剖面圖，圖1(b)是表示圖1(a)的A-A剖面圖的圖。 Fig. 1(a) is a schematic enlarged cross-sectional view showing a heat transfer tube of the present invention, and Fig. 1(b) is a view showing a cross-sectional view taken along line A-A of Fig. 1(a).

圖2(a)是表示包含本發明的傳熱管的傳熱管列單元的平面圖，圖2(b)是表示該平面圖的B-B線剖面圖的圖。 Fig. 2 (a) is a plan view showing a heat transfer tube row unit including the heat transfer tube of the present invention, and Fig. 2 (b) is a view showing a cross-sectional view taken along line B-B of the plan view.

圖3是圖2所示的傳熱管列單元的C-C側剖面圖。 Fig. 3 is a cross-sectional side view taken along line C-C of the heat transfer tube row unit shown in Fig. 2;

圖4是圖2(b)所示的剖面圖的局部放大剖面圖。 Fig. 4 is a partially enlarged cross-sectional view showing the sectional view shown in Fig. 2(b).

圖5是另一實施方式的傳熱管的剖面圖。 Fig. 5 is a cross-sectional view showing a heat transfer tube according to another embodiment.

圖6(a)是本發明的傳熱管的示意放大剖面圖，圖6(b)是圖6(a)的A-A剖面圖。 Fig. 6 (a) is a schematic enlarged cross-sectional view of a heat transfer tube of the present invention, and Fig. 6 (b) is a cross-sectional view taken along line A-A of Fig. 6 (a).

圖7(a)是包含本發明的傳熱管的傳熱管列單元的平面圖，圖7(b)是與一次分支管正交且包含內管的軸線的面的剖面圖。 Fig. 7 (a) is a plan view showing a heat transfer tube array unit including the heat transfer tube of the present invention, and Fig. 7 (b) is a cross-sectional view of a surface orthogonal to the primary branch tube and including the axis of the inner tube.

圖8是從二次分支管的內方觀察到的外管及內管的正面圖。 Fig. 8 is a front elevational view of the outer tube and the inner tube as seen from the inside of the secondary branch pipe.

圖9是圖7(b)的主要部分放大圖。 Fig. 9 is an enlarged view of a main part of Fig. 7(b).

圖10(a)是包括將帶板每隔規定長度扭轉90度而成形的傳熱構件的傳熱管的剖面圖，圖10(b)是圖10(a)的B-B剖面圖，圖10(c)是圖10(a)的C-C剖面圖。 Fig. 10 (a) is a cross-sectional view of a heat transfer tube including a heat transfer member formed by twisting a strip plate by a predetermined length by 90 degrees, and Fig. 10 (b) is a cross-sectional view taken along line BB of Fig. 10 (a), Fig. 10 ( c) is a CC cross-sectional view of Fig. 10(a).

圖11是圖10(a)至圖10(c)所示的傳熱構件的立體圖。 Fig. 11 is a perspective view of the heat transfer member shown in Figs. 10(a) to 10(c).

圖12是使圓桿的外徑變形為橢圓形而每隔規定長度改變90度朝向的外周部凸出圓桿的立體圖。 Fig. 12 is a perspective view of the outer peripheral protruding round bar in which the outer diameter of the round bar is deformed into an elliptical shape and the orientation is changed by 90 degrees every predetermined length.

圖13(a)是包括圖12的外周部凸出圓桿的傳熱管的剖面圖，圖13(b)是圖13(a)的D-D剖面圖，圖13(c)是圖13(a)的E-E剖面圖，圖13(d)是圖13(a)的F-F剖面圖。 Figure 13 (a) is a cross-sectional view of a heat transfer tube including the outer peripheral projecting round bar of Figure 12, Figure 13 (b) is a DD cross-sectional view of Figure 13 (a), Figure 13 (c) is Figure 13 (a) The EE cross-sectional view of Fig. 13(d) is the FF cross-sectional view of Fig. 13(a).

圖14(a)是包括大徑部與小徑部交替地形成的異徑圓桿的傳熱管的剖面圖，圖14(b)是圖14(a)的G-G剖面圖，圖14(c)是圖14(a)的H-H剖面圖。 Fig. 14 (a) is a cross-sectional view of a heat transfer tube including a reduced diameter round rod in which a large diameter portion and a small diameter portion are alternately formed, and Fig. 14 (b) is a GG sectional view of Fig. 14 (a), Fig. 14 (c) ) is a cross-sectional view of HH of Fig. 14(a).

圖15(a)是包括大徑部與小徑部由平緩的面形成的具有收縮部的圓桿的傳熱管的剖面圖，圖15(b)是圖15(a)的I-I剖面圖，圖15(c)是圖15(a)的J-J剖面圖。 Fig. 15 (a) is a cross-sectional view of a heat transfer tube including a round bar having a constricted portion formed of a flat surface of a large diameter portion and a small diameter portion, and Fig. 15 (b) is a cross-sectional view taken along line II of Fig. 15 (a). Fig. 15 (c) is a cross-sectional view taken along line JJ of Fig. 15 (a).

圖16(a)是包括剖面是多邊形狀的實心桿的傳熱管的剖面圖，圖16(b)是圖16(a)的K-K剖面圖。 Fig. 16 (a) is a cross-sectional view of a heat transfer tube including a solid rod having a polygonal cross section, and Fig. 16 (b) is a cross-sectional view taken along line K-K of Fig. 16 (a).

圖17是包括圓桿型的各所述形狀例中將端部形成為流線型的傳熱構件的傳熱管的剖面圖。 Fig. 17 is a cross-sectional view showing a heat transfer tube in which the end portion is formed into a streamlined heat transfer member in each of the shape examples of the round bar type.

圖18是使用本發明的傳熱管而構成的熱交換器的立體圖。 Fig. 18 is a perspective view of a heat exchanger constructed using the heat transfer tube of the present invention.

圖19是使用本發明的傳熱管而構成的另一實施方式的熱交換器的示意分解立體圖。 Fig. 19 is a schematic exploded perspective view of a heat exchanger according to another embodiment of the heat transfer tube of the present invention.

圖20是圖19所示的熱交換器的側剖面圖。 Figure 20 is a side cross-sectional view of the heat exchanger shown in Figure 19.

首先，參照附圖對本發明的第一實施方式進行說明。 First, a first embodiment of the present invention will be described with reference to the drawings.

圖1(a)是表示本發明的傳熱管的示意放大剖面圖，圖1(b)是表示圖1(a)的A-A剖面圖的圖，圖2(a)是表示包含本發明的傳熱管的熱交換器的傳熱管列單元的平面圖，圖2(b)是表示該平面圖的B-B線剖面圖的圖，圖3是圖2(a)、圖2(b)所示的傳熱管列單元的C-C側剖面圖，圖4是圖2(b)所示的剖面圖的局部放大剖面圖。 Fig. 1 (a) is a schematic enlarged cross-sectional view showing a heat transfer tube of the present invention, Fig. 1 (b) is a view showing a cross-sectional view taken along line AA of Fig. 1 (a), and Fig. 2 (a) is a view showing a pass of the present invention. FIG. 2(b) is a plan view showing a heat transfer tube array unit of the heat exchanger of the heat pipe, and FIG. 2(b) is a cross-sectional view taken along line BB of the plan view, and FIG. 3 is a view showing the transfer shown in FIGS. 2(a) and 2(b). 4 is a cross-sectional view of the heat pipe array unit, and FIG. 4 is a partially enlarged cross-sectional view of the cross-sectional view shown in FIG. 2(b).

本實施方式的傳熱管11包括外管13、內管15、間隙支撐構件17、及支撐構件19。 The heat transfer tube 11 of the present embodiment includes an outer tube 13, an inner tube 15, a gap support member 17, and a support member 19.

外管13包含筆直的細管，內管15***至外管13，且兩端從該外管13的兩端導出。此外，內管15與外管13設為同軸心狀態。 The outer tube 13 includes a straight thin tube, and the inner tube 15 is inserted into the outer tube 13, and both ends are led out from both ends of the outer tube 13. Further, the inner tube 15 and the outer tube 13 are in a concentric state.

該傳熱管11由多根構成，且以成為同一平面狀的方式平行地排列而相互鄰接地並列著，從而構成成為矩形狀的配管列且作為熱交換器的傳熱管列單元。 The heat transfer tube 11 is composed of a plurality of tubes, and is arranged in parallel so as to be flush with each other so as to be parallel to each other, thereby constituting a rectangular tube array and serving as a heat transfer tube row unit of the heat exchanger.

並列配置的所有內管15的入口端上連接著一次分支管21，一次分支管21的一端利用栓塞23而閉合。所有外管13的入口端上連接著二次分支管25，二次分支管25的一端利用栓塞23而閉合，且所述內管15貫通。所有內管15的出口端上連接著一次集合管27，一次集合管27的另一端利用栓塞23而閉合。所有外管13的出口端上連接著二次集合管29，二次集合管29的另一端利用栓塞23而閉合，且內管15貫通。本實施方式中，一次分支管21、一次集合管27、二次分支管25、及二次集合管29包含筆直的圓管。 The branch end 21 is connected to the inlet end of all the inner tubes 15 arranged in parallel, and one end of the primary branch tube 21 is closed by the plug 23. The secondary branch pipe 25 is connected to the inlet end of all the outer pipes 13, and one end of the secondary branch pipe 25 is closed by the plug 23, and the inner pipe 15 is penetrated. A collecting tube 27 is connected to the outlet end of all the inner tubes 15, and the other end of the primary collecting tube 27 is closed by the plug 23. The secondary collecting pipe 29 is connected to the outlet end of all the outer tubes 13, and the other end of the secondary collecting pipe 29 is closed by the plug 23, and the inner tube 15 is penetrated. In the present embodiment, the primary branch pipe 21, the primary collecting pipe 27, the secondary branch pipe 25, and the secondary collecting pipe 29 include straight round pipes.

內管15外周面與外管13內周面之間具有作為流路的間隙31，在該間隙部分***間隙支撐構件17。間隙支撐構件17為由與間隙長度(間 隙幅長)W大致相等的線徑d1構成的捲材，其中所述間隙長度(間隙幅長)W是外管13的內周面與內管15的外周面的間隙長度。也就是，包含捲材的間隙支撐構件17的捲內徑D1設為內管15的外徑D5(D1=D5)，捲外徑D2設為外管13的內徑D4(D2=D4)，螺旋狀地與外管13的內周面及內管15的外周面接觸，且隔著與線徑d1同等長度的間隙長度(間隙幅長)W(d1=W=D4-D5)來配置外管13與內管15，從而可遍及外管13的大致全長來支撐內管15與外管13。 A gap 31 as a flow path is provided between the outer circumferential surface of the inner tube 15 and the inner circumferential surface of the outer tube 13, and the gap support member 17 is inserted into the gap portion. The gap support member 17 is made up of the gap length (between A web composed of a wire diameter d1 having a substantially equal width W, wherein the gap length (gap length) W is a gap length between the inner circumferential surface of the outer tube 13 and the outer circumferential surface of the inner tube 15. That is, the roll inner diameter D1 of the gap supporting member 17 including the coil is set to the outer diameter D5 (D1=D5) of the inner tube 15, and the outer diameter D2 of the outer tube 13 is set to the inner diameter D4 of the outer tube 13 (D2=D4), The outer peripheral surface of the outer tube 13 and the outer peripheral surface of the inner tube 15 are spirally contacted, and the gap length (gap length) W (d1 = W = D4 - D5) of the same length as the wire diameter d1 is disposed. The tube 13 and the inner tube 15 support the inner tube 15 and the outer tube 13 over substantially the entire length of the outer tube 13.

此外，在內管15中設置著與其內周面接觸的支撐構件19。支撐構件19包含設為與間隙支撐構件17大致相等的線徑d2的捲材，並且設為與內管15的內徑D6相等的捲外徑D3，且以螺旋狀地與內管15的內周面接觸而從內方支撐的方式來設置。 Further, a support member 19 that is in contact with the inner peripheral surface thereof is provided in the inner tube 15. The support member 19 includes a coil having a wire diameter d2 substantially equal to the gap support member 17, and is provided with a roll outer diameter D3 equal to the inner diameter D6 of the inner tube 15, and spirally inside the inner tube 15. The circumferential surface is contacted and set from the inner side.

如圖4所示，外管13***外管***孔33中而在二次集合管29的內側開口，所述外管***孔33穿設在二次集合管29的一管壁上。在二次集合管29的另一管壁上穿設著內管貫通孔35，插通至內管貫通孔35的內管15利用穿設在一次分支管21的內管***孔37而在一次分支管21的內側開口。 As shown in FIG. 4, the outer tube 13 is inserted into the outer tube insertion hole 33 to open inside the secondary collecting tube 29, and the outer tube insertion hole 33 is bored in a tube wall of the secondary collecting tube 29. The inner tube through hole 35 is bored in the other pipe wall of the secondary collecting pipe 29, and the inner pipe 15 inserted into the inner pipe through hole 35 is once inserted through the inner pipe insertion hole 37 of the primary branch pipe 21. The inner side of the branch pipe 21 is open.

各所述貫通部的管彼此利用焊接而氣密地固定。焊接可採用所謂放置焊料的方法，該方法是在管彼此的接觸面上放置焊料，例如放置銅焊料或黃銅焊料，並通過在爐內進行焊接而一體地接合。此外，就支撐內管15與外管13的間隙支撐構件17與支撐構件19而言，也在爐內，利用焊料而相對於外管13內周面與內管15外周面及內管15內周面進行接觸，從而使它們分別相互接合在一起。這些間隙支撐構件17、支撐構件19使用的是包含不銹鋼制的捲材且線徑為0.5 mm~2 mm的構件，該捲材是作為以螺旋狀成形的金屬絲狀的構件的捲材，且例如實施了鍍銅、鍍鎳、鍍敷所 述銅與鎳的合金或者銅與鎳的多層鍍敷等。此外，如所述般，在爐內，各捲材(間隙支撐構件17、支撐構件19)相對於外管13內周面與內管15外周面及內管15內周面進行接觸，並將鍍敷原材料作為焊料，從而使它們分別接合在一起。另外，不銹鋼制的捲材也可以是預先實施了淬火處理的具有彈簧彈性的捲材，或者也可以是未處理的捲材、也就是使筆直的金屬絲狀的原材料變形為螺旋狀而成形的捲材，優選為可廉價地構成的未處理的捲材。此外，因將外管13與內管15一起如所述般放入至爐內而進行加熱處理，所以優選使用淬火處理以前的狀態的捲材。 The tubes of the respective penetration portions are hermetically fixed by welding. The soldering may employ a so-called soldering method in which solder is placed on the contact faces of the tubes, for example, copper solder or brass solder is placed, and integrally joined by soldering in a furnace. Further, the gap supporting member 17 and the supporting member 19 for supporting the inner tube 15 and the outer tube 13 are also in the furnace, and the outer peripheral surface of the inner tube 15 and the inner tube 15 are opposed to the inner peripheral surface of the outer tube 13 by solder. The circumferential surfaces are brought into contact so that they are joined to each other. The gap support member 17 and the support member 19 are members comprising a coil made of stainless steel and having a wire diameter of 0.5 mm to 2 mm, and the coil is a coil of a wire-like member formed by a spiral shape, and For example, copper plating, nickel plating, and plating are implemented. An alloy of copper and nickel or a multilayer plating of copper and nickel. Further, as described above, in the furnace, each of the coils (gap support members 17, support members 19) is in contact with the inner peripheral surface of the inner tube 15 and the inner peripheral surface of the inner tube 15 with respect to the inner peripheral surface of the outer tube 13, and The plated raw materials are used as solder so that they are joined together. Further, the coil material made of stainless steel may be a spring-elastic coil material which has been subjected to quenching treatment in advance, or may be an untreated coil material, that is, a straight-shaped wire-like material which is deformed into a spiral shape. The coil material is preferably an untreated coil material which can be inexpensively constructed. Further, since the outer tube 13 and the inner tube 15 are placed in the furnace as described above and heat-treated, it is preferable to use a coil in a state before the quenching treatment.

另外，在將間隙支撐構件17與支撐構件19放入爐內以前，僅對內管15及外管13的端部進行點焊而臨時固定，然後組裝各管並放入至爐內，由此間隙支撐構件17、支撐構件19與內管15及外管13、且外管13、內管15、一次分支管21、二次分支管25、一次集合管27、二次集合管29分別接合在一起。 Further, before the gap supporting member 17 and the supporting member 19 are placed in the furnace, only the ends of the inner tube 15 and the outer tube 13 are spot-welded and temporarily fixed, and then the tubes are assembled and placed in the furnace. The gap support member 17, the support member 19 and the inner tube 15 and the outer tube 13, and the outer tube 13, the inner tube 15, the primary branch tube 21, the secondary branch tube 25, the primary collecting tube 27, and the secondary collecting tube 29 are respectively joined together.

如圖3所示，外管13在二次分支管25的內部開口，在各個外管13的內部配置著內管15。在二次分支管25中從外管13導出的內管15在貫通二次分支管25後，在一次集合管27的內部分別開口。插通著內管15的多根外管13、連接於外管13的兩端的二次分支管25及二次集合管29、以及連接於內管15的兩端的一次分支管21及一次集合管27，在同一平面上形成成為四邊形狀的圖2(a)所示的傳熱管列單元39。 As shown in FIG. 3, the outer tube 13 is opened inside the secondary branch pipe 25, and the inner tube 15 is disposed inside each outer tube 13. The inner tube 15 which is led out from the outer tube 13 in the secondary branch pipe 25 is opened inside the primary collecting pipe 27 after passing through the secondary branch pipe 25. a plurality of outer tubes 13 through which the inner tube 15 is inserted, a secondary branch tube 25 and a secondary collecting tube 29 connected to both ends of the outer tube 13, and a primary branch tube 21 and a primary collecting tube connected to both ends of the inner tube 15 27, a heat transfer tube row unit 39 shown in Fig. 2(a) having a quadrangular shape is formed on the same plane.

本實施方式中，傳熱管11中，內管15與外管13使用極細的金屬制圓管，內管15內的一次流路的面積S1與外管13內的二次流路的面積S2之比S1：S2設為1：2~2：1。使用如下的管：內管15的內徑設為2 mm~6 mm，優選設為3 mm~5 mm，外管13的內徑設為4 mm~10 mm，優選設為5 mm~8.5 mm，厚度設為0.15 mm~0.35 mm。 In the present embodiment, in the heat transfer tube 11, the inner tube 15 and the outer tube 13 are made of a very thin metal tube, and the area S1 of the primary flow path in the inner tube 15 and the area S2 of the secondary flow path in the outer tube 13 The ratio S1:S2 is set to 1:2~2:1. The following tube is used: the inner diameter of the inner tube 15 is set to 2 mm to 6 mm, preferably 3 mm to 5 mm, and the inner diameter of the outer tube 13 is set to 4 mm to 10 mm, preferably 5 mm to 8.5 mm. The thickness is set to 0.15 mm to 0.35 mm.

此處，例如，內管15使用的是外徑D5=4 mm、內徑D6=3.6 mm的不銹鋼(SUS)管，外管13使用的是外徑6.6 mm、內徑D4=6 mm的SUS管，而且使間隙支撐構件17及支撐構件19為線徑d1=d2=1 mm的實施了鍍銅的不銹鋼制的捲材，如果根據這些數值並根據圖1(a)及圖1(b)所示的傳熱管11的剖面(圖1(b))來求出一次流路及二次流路的面積，則一次流路的面積S1約為9.17 mm2，二次流路的面積S2約為14.70 mm2，一次流路的面積S1與二次流路的面積S2的比約為1：1.6。 Here, for example, the inner tube 15 is a stainless steel (SUS) tube having an outer diameter D5 = 4 mm and an inner diameter D6 = 3.6 mm, and the outer tube 13 is a SUS having an outer diameter of 6.6 mm and an inner diameter of D4 = 6 mm. Tube, and the gap support member 17 and the support member 19 are made of copper-plated stainless steel coil having a wire diameter d1 = d2 = 1 mm, according to these values and according to Fig. 1 (a) and Fig. 1 (b) The area of the primary flow path and the secondary flow path is obtained by the cross section of the heat transfer tube 11 (Fig. 1 (b)), and the area S1 of the primary flow path is about 9.17 mm 2 , and the area of the secondary flow path S2 It is about 14.70 mm 2 , and the ratio of the area S1 of the primary flow path to the area S2 of the secondary flow path is about 1:1.6.

另外，適當地變更所述內管15及外管13的各直徑尺寸及間隙支撐構件17、支撐構件19的各自的數值，一次流路的面積S1與二次流路的面積S2的比優選設為1：1的比，並且在包含捲材的間隙支撐構件17及支撐構件19中，剖面積根據相對於各外管13、內管15的捲數或間距而發生變化，因而可變更它們的形狀，而且通過將內管15內及外管13內的流速的比設為1：1而實現導熱率的提高。 Further, the respective diameters of the inner tube 15 and the outer tube 13 and the respective values of the gap support member 17 and the support member 19 are appropriately changed, and the ratio of the area S1 of the primary flow path to the area S2 of the secondary flow path is preferably set. In the ratio of 1:1, and in the gap supporting member 17 and the supporting member 19 including the coil, the sectional area changes depending on the number of windings or the pitch of each of the outer tubes 13 and the inner tubes 15, so that they can be changed. The shape and the ratio of the flow velocity in the inner tube 15 and the outer tube 13 are set to 1:1 to improve the thermal conductivity.

另外，所述實施方式中，關於間隙支撐構件17的形狀，表示了包含捲內徑D1及捲外徑D2設為固定的捲材的示例，但並不限定於此，例如如圖5所示，也可為大徑部41與小徑部43交替地形成的捲材。該間隙支撐構件45中設為如下構成：將線徑d1設定得小於內管15與外管13的間隙長度(間隙幅長)W，小徑部43的捲內徑D1設為內管15的外徑D5，大徑部41的捲外徑D2設為外管13的內徑D4，且在外管13內支撐內管15。根據該傳熱管11，因在內管15的外周面與外管13的內周面的間隙長度(間隙幅長)W***間隙支撐構件17的線徑d1與空隙，所以可充分地確保流路面積。 Further, in the above-described embodiment, the shape of the gap supporting member 17 is an example in which the coil inner diameter D1 and the coil outer diameter D2 are fixed, but the invention is not limited thereto, for example, as shown in FIG. The coil material which is formed alternately between the large diameter portion 41 and the small diameter portion 43 may be used. The gap support member 45 has a configuration in which the wire diameter d1 is set smaller than the gap length (gap length) W of the inner tube 15 and the outer tube 13, and the coil inner diameter D1 of the small diameter portion 43 is set as the inner tube 15. The outer diameter D5, the outer diameter D2 of the large diameter portion 41 is set to the inner diameter D4 of the outer tube 13, and the inner tube 15 is supported in the outer tube 13. According to the heat transfer tube 11, the wire diameter d1 and the gap of the gap support member 17 are inserted into the gap length (gap length) W of the outer circumferential surface of the inner tube 15 and the inner circumferential surface of the outer tube 13, so that the flow can be sufficiently ensured. Road area.

然後，參照附圖對本發明的第二實施方式進行說明。 Next, a second embodiment of the present invention will be described with reference to the drawings.

圖6(a)是本發明的傳熱管的示意放大剖面圖，圖6(b)是圖 6(a)的A-A剖面圖，圖7(a)是包含本發明的傳熱管的傳熱管列單元的平面圖，圖7(b)是與一次分支管正交且包含內管的軸線的面的剖面圖，圖8是從二次分支管的內方觀察到的外管及內管的正面圖，圖9是圖7(b)的主要部分放大圖。 Figure 6 (a) is a schematic enlarged cross-sectional view of the heat transfer tube of the present invention, and Figure 6 (b) is a view 6(a) is a cross-sectional view of AA, FIG. 7(a) is a plan view of a heat transfer tube row unit including the heat transfer tube of the present invention, and FIG. 7(b) is orthogonal to the primary branch tube and including the axis of the inner tube. Fig. 8 is a front view of the outer tube and the inner tube as seen from the inside of the secondary branch pipe, and Fig. 9 is an enlarged view of a main portion of Fig. 7(b).

本實施方式的傳熱管11包括外管13、內管15、間隙支撐構件17、支撐構件19、及傳熱構件20。 The heat transfer tube 11 of the present embodiment includes an outer tube 13, an inner tube 15, a gap support member 17, a support member 19, and a heat transfer member 20.

外管13包含筆直的細管，內管15***至外管13，且兩端從該外管13的兩端導出。此外，內管15與外管13設為同軸心狀態。 The outer tube 13 includes a straight thin tube, and the inner tube 15 is inserted into the outer tube 13, and both ends are led out from both ends of the outer tube 13. Further, the inner tube 15 and the outer tube 13 are in a concentric state.

該傳熱管11由多根構成，且以成為同一平面狀的方式平行地排列而相互鄰接地並列著，從而構成成為矩形狀的配管列的傳熱管列單元39。 The heat transfer tube 11 is composed of a plurality of tubes, and is arranged in parallel so as to be flush with each other, and is arranged adjacent to each other to constitute a heat transfer tube array unit 39 which is a rectangular tube array.

並列配置的所有內管15的入口端上連接著一次分支管21，一次分支管21的一端利用栓塞23而閉合。所有外管13的入口端上連接著二次分支管25，二次分支管25的一端利用栓塞23而閉合，且所述內管15貫通。所有內管15的出口端上連接著一次集合管27，一次集合管27的另一端利用栓塞23而閉合。所有外管13的出口端上連接著二次集合管29，二次集合管29的另一端利用栓塞23而閉合，且內管15貫通。本實施方式中，一次分支管21、一次集合管27、二次分支管25及二次集合管29包含筆直的圓管。 The branch end 21 is connected to the inlet end of all the inner tubes 15 arranged in parallel, and one end of the primary branch tube 21 is closed by the plug 23. The secondary branch pipe 25 is connected to the inlet end of all the outer pipes 13, and one end of the secondary branch pipe 25 is closed by the plug 23, and the inner pipe 15 is penetrated. A collecting tube 27 is connected to the outlet end of all the inner tubes 15, and the other end of the primary collecting tube 27 is closed by the plug 23. The secondary collecting pipe 29 is connected to the outlet end of all the outer tubes 13, and the other end of the secondary collecting pipe 29 is closed by the plug 23, and the inner tube 15 is penetrated. In the present embodiment, the primary branch pipe 21, the primary collecting pipe 27, the secondary branch pipe 25, and the secondary collecting pipe 29 include straight round pipes.

如圖6(a)所示，內管外周面30與外管內周面32之間具有成為流路的間隙31，在該間隙部分***間隙支撐構件17。間隙支撐構件17為由與間隙長度(間隙幅長)W大致相等的線徑d1構成的捲材，其中所述間隙長度(間隙幅長)是外管13的內周面與內管15的外周面的間隙長度。也就是，包含捲材的間隙支撐構件17的捲內徑D1設為內管15的外徑D5(D1=D5)，捲外徑D2設為外管13的內徑D4(D2=D4)，螺旋狀地與外管 13的內周面及內管15的外周面接觸，且隔著與線徑d1同等長度的間隙長度(間隙幅長)W(d1=W=(D4-D5)/2)來配置外管13及內管15，從而可遍及外管13的大致全長來支撐內管15與外管13。 As shown in Fig. 6(a), a gap 31 which is a flow path is provided between the inner tube outer peripheral surface 30 and the outer tube inner peripheral surface 32, and the gap supporting member 17 is inserted into the gap portion. The gap supporting member 17 is a web composed of a wire diameter d1 substantially equal to the gap length (gap length) W, wherein the gap length (gap length) is the inner peripheral surface of the outer tube 13 and the outer circumference of the inner tube 15. The length of the gap. That is, the roll inner diameter D1 of the gap supporting member 17 including the coil is set to the outer diameter D5 (D1=D5) of the inner tube 15, and the outer diameter D2 of the outer tube 13 is set to the inner diameter D4 of the outer tube 13 (D2=D4), Spiral and outer tube The inner peripheral surface of the inner peripheral surface of the inner tube 15 is in contact with each other, and the outer tube 13 is disposed with a gap length (gap length) W (d1 = W = (D4 - D5) / 2) of the same length as the wire diameter d1. And the inner tube 15, so that the inner tube 15 and the outer tube 13 can be supported over substantially the entire length of the outer tube 13.

此外，在內管15中設置著與其內周面接觸的支撐構件19。支撐構件19包含設為與間隙支撐構件17大致相等的線徑d2的捲材，並且設為與內管15的內徑D6相等的捲外徑D3，且以螺旋狀地與內管15的內周面接觸而從內方支撐的方式設置。 Further, a support member 19 that is in contact with the inner peripheral surface thereof is provided in the inner tube 15. The support member 19 includes a coil having a wire diameter d2 substantially equal to the gap support member 17, and is provided with a roll outer diameter D3 equal to the inner diameter D6 of the inner tube 15, and spirally inside the inner tube 15. It is set by means of internal support in the case of circumferential contact.

在支撐構件19的中心設置著傳熱構件20。傳熱構件20遍及支撐構件19的全長而設置，至少外周的一部分與支撐構件19接觸。本實施方式中，該傳熱構件20為在支撐構件19的長度方向上是長的且螺旋狀地扭轉的帶板141。帶板141的幅長與支撐構件19的內徑D7大致相等。 A heat transfer member 20 is disposed at the center of the support member 19. The heat transfer member 20 is provided over the entire length of the support member 19, and at least a part of the outer circumference is in contact with the support member 19. In the present embodiment, the heat transfer member 20 is a strip plate 141 that is long and spirally twisted in the longitudinal direction of the support member 19. The web 141 has a web length substantially equal to the inner diameter D7 of the support member 19.

外管13***穿設在二次分支管25、二次集合管29的一管壁的外管***孔33而在二次分支管25、二次集合管29的內側開口。在二次分支管25、二次集合管29的另一管壁穿設著內管貫通孔35，插通至內管貫通孔35的內管15利用穿設在一次分支管21、一次集合管27的內管***孔37而在一次分支管21、一次集合管27的內側開口。 The outer tube 13 is inserted into the outer tube insertion hole 33 penetrating the tube wall of the secondary branch tube 25 and the secondary collecting tube 29, and is opened inside the secondary branch tube 25 and the secondary collecting tube 29. The inner tube through hole 35 is bored in the other tube wall of the secondary branch pipe 25 and the secondary collecting pipe 29, and the inner pipe 15 inserted into the inner pipe through hole 35 is bored in the primary branch pipe 21 and the primary collecting pipe. The inner tube of the 27 is inserted into the hole 37 and opened inside the primary branch pipe 21 and the primary collecting pipe 27.

各所述貫通部的管彼此利用焊接而氣密地固定。焊接可採用所謂放置焊料的方法，該方法是在管彼此的接觸面上放置焊料，例如放置銅焊料或黃銅焊料，並通過在爐內進行焊接而一體地接合。此外，就支撐內管15與外管13的間隙支撐構件17、支撐構件19及傳熱構件20而言，也在爐內，利用焊料相對於外管內周面32與內管外周面30及內管內周面38進行接觸，而使它們分別相互接合在一起。這些間隙支撐構件17或支撐構件19使用的是包含不銹鋼制的捲材且線徑為0.5 mm~2 mm的構件，該捲材是作為螺旋狀成形的金屬絲狀的構件的捲材，且例如實施了鍍銅、鍍鎳、 鍍敷所述銅與鎳的合金或者銅與鎳的多層鍍敷等。此外，如所述般，在爐內，間隙支撐構件17與支撐構件19相對於外管內周面32與內管外周面30及內管內周面38(參照圖6(a))、傳熱構件20進行接觸，並將鍍敷原材料作為焊料，從而使它們分別接合在一起。另外，不銹鋼制的捲材也可以是預先實施了淬火處理的具有彈簧彈性的捲材，或者也可以是未處理的捲材、也就是使筆直的金屬絲狀的原材料變形為螺旋狀而成形的捲材，優選為可廉價地構成的未處理的捲材。此外，因將外管13與內管15一起如所述般放入至爐內而進行加熱處理，所以優選使用淬火處理以前的狀態的捲材。 The tubes of the respective penetration portions are hermetically fixed by welding. The soldering may employ a so-called soldering method in which solder is placed on the contact faces of the tubes, for example, copper solder or brass solder is placed, and integrally joined by soldering in a furnace. Further, in the case of supporting the gap support member 17, the support member 19, and the heat transfer member 20 of the inner tube 15 and the outer tube 13, the inner peripheral surface 32 of the outer tube and the inner peripheral surface 30 of the inner tube are also used in the furnace. The inner peripheral surface 38 of the inner tube is brought into contact so that they are joined to each other, respectively. The gap supporting member 17 or the supporting member 19 is a member comprising a coil made of stainless steel and having a wire diameter of 0.5 mm to 2 mm, which is a coil of a wire-shaped member which is formed in a spiral shape, and for example Implemented copper plating, nickel plating, The alloy of copper and nickel or the multilayer plating of copper and nickel is plated. Further, as described above, in the furnace, the gap support member 17 and the support member 19 are transmitted to the inner tube inner peripheral surface 32, the inner tube outer peripheral surface 30, and the inner tube inner peripheral surface 38 (see Fig. 6(a)). The heat member 20 makes contact and uses the plating raw material as a solder so that they are joined together, respectively. Further, the coil material made of stainless steel may be a spring-elastic coil material which has been subjected to quenching treatment in advance, or may be an untreated coil material, that is, a straight-shaped wire-like material which is deformed into a spiral shape. The coil material is preferably an untreated coil material which can be inexpensively constructed. Further, since the outer tube 13 and the inner tube 15 are placed in the furnace as described above and heat-treated, it is preferable to use a coil in a state before the quenching treatment.

另外，在間隙支撐構件17、支撐構件19、傳熱構件20放入爐內以前，僅對內管15及外管13的端部進行點焊而臨時固定，然後組裝內管15及外管13而可放入至爐內。由此，內管15與支撐構件19、支撐構件19與傳熱構件20、內管15與間隙支撐構件17及外管13、一次分支管21與內管15、一次集合管27與內管15、二次分支管25與外管13、二次集合管29與外管13分別接合。 Further, before the gap support member 17, the support member 19, and the heat transfer member 20 are placed in the furnace, only the ends of the inner tube 15 and the outer tube 13 are spot-welded and temporarily fixed, and then the inner tube 15 and the outer tube 13 are assembled. It can be placed in the furnace. Thereby, the inner tube 15 and the support member 19, the support member 19 and the heat transfer member 20, the inner tube 15 and the gap support member 17 and the outer tube 13, the primary branch tube 21 and the inner tube 15, the primary collecting tube 27 and the inner tube 15 The secondary branch pipe 25 and the outer pipe 13, the secondary manifold 29 and the outer pipe 13 are joined, respectively.

如圖8所示，外管13在二次分支管25的內部開口，在各個外管13的內部配置著內管15。在二次分支管25中從外管13導出的內管15在貫通二次分支管25後，在一次集合管27的內部分別開口。插通著內管15的多根外管13、連接於外管13的兩端的二次分支管25及二次集合管29、以及連接於內管15的兩端的一次分支管21及一次集合管27，在同一平面上形成成為四邊形狀的圖7(a)所示的傳熱管列單元39。 As shown in FIG. 8, the outer tube 13 is opened inside the secondary branch pipe 25, and the inner tube 15 is disposed inside each outer tube 13. The inner tube 15 which is led out from the outer tube 13 in the secondary branch pipe 25 is opened inside the primary collecting pipe 27 after passing through the secondary branch pipe 25. a plurality of outer tubes 13 through which the inner tube 15 is inserted, a secondary branch tube 25 and a secondary collecting tube 29 connected to both ends of the outer tube 13, and a primary branch tube 21 and a primary collecting tube connected to both ends of the inner tube 15 27, a heat transfer tube row unit 39 shown in Fig. 7(a) having a quadrangular shape is formed on the same plane.

本實施方式中，傳熱管11中，內管15與外管13使用極細的金屬制圓管。內管15的一次流路的面積S1為(內管15的內徑剖面積-支撐構件的剖面積-帶板的剖面積)。此外，外管13的二次流路的面積S2為(外管 13的內徑剖面積-內管的外徑剖面積-間隙支撐構件的剖面積)。一次流路的面積S1與二次流路的面積S2的比設為S1：S2=1：2~2：1。使用如下的管：內管15的內徑設為2 mm~6 mm，優選設為3 mm~5 mm，外管13的內徑設為4 mm~10 mm，優選設為5 mm~8.5 mm，厚度設為0.15 mm~0.35 mm。 In the present embodiment, in the heat transfer tube 11, the inner tube 15 and the outer tube 13 are made of a very thin metal round tube. The area S1 of the primary flow path of the inner tube 15 is (the inner diameter sectional area of the inner tube 15 - the sectional area of the support member - the sectional area of the strip). In addition, the area S2 of the secondary flow path of the outer tube 13 is (outer tube) The inner diameter sectional area of 13 - the outer diameter sectional area of the inner tube - the sectional area of the gap support member). The ratio of the area S1 of the primary flow path to the area S2 of the secondary flow path is set to S1:S2=1:2 to 2:1. The following tube is used: the inner diameter of the inner tube 15 is set to 2 mm to 6 mm, preferably 3 mm to 5 mm, and the inner diameter of the outer tube 13 is set to 4 mm to 10 mm, preferably 5 mm to 8.5 mm. The thickness is set to 0.15 mm to 0.35 mm.

此處，例如，內管15使用外徑D5=4 mm、內徑D6=3.6 mm的SUS管，外管13使用外徑6.6 mm、內徑D4=6 mm的SUS管，而且將間隙支撐構件17及支撐構件19設為線徑d1=d2=1 mm的實施了鍍銅的不銹鋼制的捲材，帶板141設為幅長1.6 mm、厚度0.21 mm，如果根據這些數值並根據圖6(a)及圖6(b)所示的傳熱管11的剖面(圖6(b))來求出一次流路的面積S1與二次流路的面積S2的面積，則一次流路的面積S1約為8.5 mm2，二次流路的面積S2約為14.0 mm2，一次流路的面積S1與二次流路的面積S2的比約為1：1.65。 Here, for example, the inner tube 15 uses a SUS tube having an outer diameter D5 = 4 mm and an inner diameter D6 = 3.6 mm, and the outer tube 13 uses a SUS tube having an outer diameter of 6.6 mm and an inner diameter D4 = 6 mm, and the gap supporting member is used. 17 and the support member 19 are made of a copper-plated stainless steel coil having a wire diameter d1 = d2 = 1 mm, and the strip 141 is set to have a length of 1.6 mm and a thickness of 0.21 mm, according to these values and according to Fig. 6 ( a) and the cross section of the heat transfer tube 11 shown in Fig. 6(b) (Fig. 6(b)), the area of the primary flow path S1 and the area of the secondary flow path S2 are obtained, and the area of the primary flow path is obtained. S1 is approximately 8.5 mm 2 , the area S2 of the secondary flow path is approximately 14.0 mm 2 , and the ratio of the area S1 of the primary flow path to the area S2 of the secondary flow path is approximately 1:1.65.

另外，適當地變更所述內管15及外管13的各直徑尺寸及間隙支撐構件17、支撐構件19、帶板141的各自的數值，一次流路的面積S1與二次流路的面積S2的比優選設為1：1的比，並且在包含捲材的間隙支撐構件17及支撐構件19中，剖面積根據相對於內管15及外管13的捲數或間距而發生變化，因而可變更它們的形狀，而且通過將內管15及外管13的流速的比設為1：1而實現導熱率的提高。 Further, the respective diameters of the inner tube 15 and the outer tube 13 and the respective values of the gap support member 17, the support member 19, and the strip 141, the area S1 of the primary flow path and the area S2 of the secondary flow path are appropriately changed. The ratio is preferably set to a ratio of 1:1, and in the gap supporting member 17 and the supporting member 19 including the coil, the sectional area changes depending on the number of windings or the interval with respect to the inner tube 15 and the outer tube 13, and thus The shape is changed, and the ratio of the flow rates of the inner tube 15 and the outer tube 13 is set to 1:1 to improve the thermal conductivity.

對所述傳熱管11的作用說明。 The action of the heat transfer tube 11 will be described.

內管15中流動的熱媒一邊與設置在內管15的內側的傳熱構件20及支撐構件19接觸一邊流動，以前，僅與內管內周面38接觸的熱媒的接觸面積增大。熱媒通過與傳熱構件20及支撐構件19進行接觸，而利用熱傳遞與傳熱構件20、支撐構件19進行熱交換。經熱交換的熱量利用熱傳 導而傳遞至內管15，且與在外管13與內管15的間隙31內流動的另一系統的熱媒進行熱交換。也就是，在內管15內交換的熱量有助於重新提高熱交換效率。 The heat medium flowing through the inner tube 15 flows while being in contact with the heat transfer member 20 and the support member 19 provided inside the inner tube 15, and previously, the contact area of only the heat medium that is in contact with the inner peripheral surface 38 of the inner tube is increased. The heat medium is in contact with the heat transfer member 20 and the support member 19, and exchanges heat with the heat transfer member 20 and the support member 19 by heat transfer. Heat exchange heat transfer It is transferred to the inner tube 15 and exchanges heat with the heat medium of another system flowing in the gap 31 between the outer tube 13 and the inner tube 15. That is, the heat exchanged in the inner tube 15 contributes to a renewed heat exchange efficiency.

此外，作為傳熱構件20的帶板141一邊與支撐構件20接觸一邊設置為螺旋狀，支撐構件19呈捲狀地配設在內管15內，內管15內流動的熱媒一邊螺旋旋轉或蜿蜒一邊在內管15中前進。由此，相比於熱媒與軸線平行地筆直流動的情況，可增大熱媒在內管15內接觸的接觸面積及接觸時間。因為是廉價的材料，所以不會相對地增大流動損失，從而可提高內管15與在該內管15中流動的熱媒的熱交換率。 Further, the belt plate 141 as the heat transfer member 20 is provided in a spiral shape while being in contact with the support member 20, and the support member 19 is disposed in a roll shape in the inner tube 15, and the heat medium flowing in the inner tube 15 is spirally rotated or The crucible advances in the inner tube 15. Thereby, the contact area and the contact time of the contact of the heat medium in the inner tube 15 can be increased as compared with the case where the heat medium flows straight in parallel with the axis. Since it is an inexpensive material, the flow loss is not relatively increased, so that the heat exchange rate of the inner tube 15 and the heat medium flowing in the inner tube 15 can be increased.

圖10(a)是包括將帶板每隔規定長度而扭轉90度成形的傳熱構件的傳熱管的剖面圖，圖10(b)是圖10(a)的B-B剖面圖，圖10(c)是圖10(a)的C-C剖面圖，圖11是圖10(a)至圖10(c)所示的傳熱構件的立體圖。 Fig. 10 (a) is a cross-sectional view of a heat transfer tube including a heat transfer member formed by twisting a strip plate by a predetermined length by 90 degrees, and Fig. 10 (b) is a cross-sectional view taken along line BB of Fig. 10 (a), Fig. 10 ( c) is a CC cross-sectional view of Fig. 10 (a), and Fig. 11 is a perspective view of the heat transfer member shown in Figs. 10 (a) to 10 (c).

傳熱構件20也可設為如下構成：將規定長度的長方形板以兩端例如擰轉180°而成形細長的螺旋形的帶板141，且每隔規定長度例如扭轉90度而將端部彼此連結成形。該情況下，可隔著通過帶板141的寬度方向中央的軸線，從寬度方向的兩側預先開設切口151，由此使姿勢以每90度反轉而成形。根據該構成，將熱媒連同位於帶板141的外周的支撐構件19在內管15內進行攪拌而可增加接觸面積以使其接觸。另外，所述帶板141的擰轉角度的180°及扭轉角度的90度並不限定於這些，也可將擰轉角度設為90°或120°等其他角度，而且也可將扭轉角度設定為45度或60度等其他角度來成形。 The heat transfer member 20 may be configured such that a rectangular plate having a predetermined length is twisted by 180° at both ends to form an elongated spiral strip 141, and the end portions are twisted by 90 degrees every predetermined length, for example. The joint is formed. In this case, the slit 151 is opened in advance from both sides in the width direction through the axis passing through the center in the width direction of the strip 141, whereby the posture is reversed every 90 degrees. According to this configuration, the heat medium and the support member 19 located on the outer periphery of the strip plate 141 are stirred in the inner tube 15 to increase the contact area to make contact. Further, the twist angle of the belt plate 141 and the twist angle of 90 degrees are not limited to these, and the twist angle may be set to other angles such as 90° or 120°, and the twist angle may be set. Formed at other angles such as 45 degrees or 60 degrees.

圖12是使圓桿的外徑變形為橢圓形而每隔規定長度改變90度朝向的外周部凸出圓桿的立體圖，圖13(a)是包括圖12的外周部凸出圓 桿的傳熱管的剖面圖，圖13(b)是圖13(a)的D-D剖面圖，圖13(c)是圖13(a)的E-E剖面圖，圖13(d)是圖13(a)的F-F剖面圖。 Fig. 12 is a perspective view of the outer peripheral protruding round bar in which the outer diameter of the round bar is deformed into an elliptical shape and changed by 90 degrees every predetermined length, and Fig. 13(a) is a convex portion including the outer peripheral portion of Fig. 12. A cross-sectional view of the heat transfer tube of the rod, Fig. 13(b) is a DD cross-sectional view of Fig. 13(a), Fig. 13(c) is an EE cross-sectional view of Fig. 13(a), and Fig. 13(d) is Fig. 13 ( a) FF section view.

傳熱構件20可形成為具有長圓部155的外周部凸出圓桿153，該長圓部155是在支撐構件19的長度方向上每隔規定間隔向徑向擠壓圓形外周變形所得。通過以從軸線正交方向夾持圓桿原材料的方式受到擠壓，被擠壓的部分向半徑方向外側凸出，從而成為長圓部155。該長圓部155的凸出前端側與支撐構件19接觸。該擠壓方向例如每90度交替地改變，由此對熱媒的流路進行攪拌且可使其蜿蜒。例如，內管15設為外徑D5=4.4 mm、內徑D6=4.0 mm，外管13設為外徑6.6 mm、內徑D4=6 mm，間隙支撐構件17設為線徑d1=0.8 mm，支撐構件19設為線徑d2=1 mm，外周部凸出圓桿153的剖面積設為1.77 mm2，如果根據這些數值並根據圖13(a)至圖13(d)所示的傳熱管11的剖面(圖13(b)、圖13(c)、圖13(d))來求出一次流路的面積S1與二次流路的面積S2的面積，則一次流路的面積S1約為9.5 mm2，二次流路的面積S2約為12.1 mm2，一次流路的面積S1與二次流路的面積S2的比約為1：1.27。 The heat transfer member 20 can be formed as an outer peripheral portion projecting round bar 153 having an oblong portion 155 which is deformed by pressing a circular outer circumference at a predetermined interval in the longitudinal direction of the support member 19. The pressed portion is pressed outward in the radial direction from the axis orthogonal direction, and the pressed portion protrudes outward in the radial direction to form the oblong portion 155. The convex front end side of the oblong portion 155 is in contact with the support member 19. The pressing direction is alternately changed every 90 degrees, for example, thereby agitating the flow path of the heat medium and causing it to collapse. For example, the inner tube 15 has an outer diameter D5 = 4.4 mm, an inner diameter D6 = 4.0 mm, an outer tube 13 has an outer diameter of 6.6 mm, an inner diameter D4 = 6 mm, and the gap support member 17 has a wire diameter d1 = 0.8 mm. The support member 19 is set to have a wire diameter d2 = 1 mm, and the sectional area of the outer peripheral convex round bar 153 is set to 1.77 mm 2 , if according to these values and according to the figures shown in Figs. 13(a) to 13(d) The cross section of the heat pipe 11 (Fig. 13 (b), Fig. 13 (c), Fig. 13 (d))) is used to obtain the area of the primary flow path S1 and the area of the secondary flow path S2, and the area of the primary flow path. S1 is about 9.5 mm 2 , the area S2 of the secondary flow path is about 12.1 mm 2 , and the ratio of the area S1 of the primary flow path to the area S2 of the secondary flow path is about 1:1.27.

根據該傳熱構件20，可相對廉價且容易地製造具有可與內管15進行熱傳導的長圓部155的外周部凸出圓桿153。 According to the heat transfer member 20, the outer peripheral portion projecting round bar 153 having the oblong portion 155 capable of heat conduction with the inner tube 15 can be manufactured relatively inexpensively and easily.

圖14(a)是包括大徑部與小徑部交替地形成的異徑圓桿的傳熱管的剖面圖，圖14(b)是圖14(a)的G-G剖面圖，圖14(c)是圖14(a)的H-H剖面圖。 Fig. 14 (a) is a cross-sectional view of a heat transfer tube including a reduced diameter round rod in which a large diameter portion and a small diameter portion are alternately formed, and Fig. 14 (b) is a GG sectional view of Fig. 14 (a), Fig. 14 (c) ) is a cross-sectional view of HH of Fig. 14(a).

傳熱構件20可形成為異徑圓桿161，該異徑圓桿161是在支撐構件19的長度方向上每隔規定間隔使圓形外周由小徑部159與大徑部157交替形成。支撐構件19的間距與大徑部157及小徑部159的間距不同。例如，將內管15設為外徑D5=4.0 mm、內徑D6=3.6 mm，外管13設為外徑 6.6 mm、內徑D4=6 mm，間隙支撐構件17與支撐構件19設為線徑d1=d2=1 mm，異徑圓桿161的小徑部159的外徑設為0.3 mm，大徑部157的外徑設為0.9 mm，如果根據這些數值並根據圖14(a)至圖14(c)所示的傳熱管11的剖面(圖14(b)、圖14(c))來求出一次流路的面積S1與二次流路的面積S2的面積，一次流路的面積S1與二次流路的面積S2的比在大徑部157中設為S1：S2≒1：1.7，小徑部159中設為S1：S2≒1：1.6。 The heat transfer member 20 can be formed as a different diameter round rod 161 which is formed by alternately forming a circular outer circumference by a small diameter portion 159 and a large diameter portion 157 at predetermined intervals in the longitudinal direction of the support member 19. The pitch of the support member 19 is different from the pitch of the large diameter portion 157 and the small diameter portion 159. For example, the inner tube 15 is set to have an outer diameter D5 = 4.0 mm, an inner diameter D6 = 3.6 mm, and the outer tube 13 is set to an outer diameter. 6.6 mm, inner diameter D4=6 mm, the gap support member 17 and the support member 19 are set to have a wire diameter d1=d2=1 mm, and the outer diameter of the small diameter portion 159 of the reducer rod 161 is set to 0.3 mm, and the large diameter portion The outer diameter of 157 is set to 0.9 mm, and based on these values and according to the cross section of the heat transfer tube 11 shown in Figs. 14(a) to 14(c) (Fig. 14(b), Fig. 14(c)) The area of the area S1 of the primary flow path and the area S2 of the secondary flow path, the ratio of the area S1 of the primary flow path to the area S2 of the secondary flow path is set to S1:S2≒1:1.7 in the large diameter portion 157. The small diameter portion 159 is set to S1:S2≒1:1.6.

根據該傳熱構件20，通過將異徑圓桿161***至內管15，沿著異徑圓桿161流動的熱媒一邊與大徑部157碰撞一邊流動。因該碰撞而打亂熱媒的流動，對內管15中流動的熱媒進行攪拌，在不與內管內周面38或支撐構件19、傳熱構件20接觸的狀態下直接通過的熱媒得以減少，可使熱媒容易與內管15、支撐構件19及傳熱構件20進行接觸。 According to the heat transfer member 20, the reduced diameter round rod 161 is inserted into the inner tube 15, and the heat medium flowing along the different diameter round rod 161 flows while colliding with the large diameter portion 157. The flow of the heat medium is disturbed by the collision, and the heat medium flowing through the inner tube 15 is stirred, and the heat medium directly passes through the inner tube inner peripheral surface 38 or the support member 19 and the heat transfer member 20 without being in contact with each other. This can be reduced, and the heat medium can be easily brought into contact with the inner tube 15, the support member 19, and the heat transfer member 20.

圖15(a)是包括大徑部與小徑部由平緩的面形成的具有收縮部的圓桿的傳熱管的剖面圖，圖15(b)是圖15(a)的I-I剖面圖，圖15(c)是圖15(a)的J-J剖面圖。 Fig. 15 (a) is a cross-sectional view of a heat transfer tube including a round bar having a constricted portion formed of a flat surface of a large diameter portion and a small diameter portion, and Fig. 15 (b) is a cross-sectional view taken along line II of Fig. 15 (a). Fig. 15 (c) is a cross-sectional view taken along line JJ of Fig. 15 (a).

傳熱構件20可形成為圓桿163，該圓桿163是將大徑部157與小徑部159由平緩的面形成且具有收縮部。例如，將內管15設為外徑D5=4.4 mm、內徑D6=4.0 mm，外管13設為外徑6.6 mm、內徑D4=6 mm，間隙支撐構件17設為線徑d1=0.8 mm，支撐構件19設為線徑d2=1 mm，具有收縮部的圓桿163的小徑部159的外徑設為0.76 mm，大徑部157的外徑設為2.0 mm，如果根據這些數值並根據圖15(a)至圖15(c)所示的傳熱管11的剖面(圖15(b)、圖15(c))來求出一次流路的面積S1與二次流路的面積S2的面積，則一次流路的面積S1與二次流路的面積S2的比在大徑部157中設為S1：S2≒1：1.47，在小徑部159中設為S1：S2≒1：1.11。 The heat transfer member 20 may be formed as a round bar 163 which is formed by a flat surface of the large diameter portion 157 and the small diameter portion 159 and has a constricted portion. For example, the inner tube 15 is set to have an outer diameter D5 = 4.4 mm, an inner diameter D6 = 4.0 mm, an outer tube 13 is set to an outer diameter of 6.6 mm, an inner diameter D4 = 6 mm, and the gap support member 17 is set to a wire diameter d1 = 0.8. Mm, the support member 19 is set to have a wire diameter d2 = 1 mm, the outer diameter of the small diameter portion 159 of the round bar 163 having the constricted portion is set to 0.76 mm, and the outer diameter of the large diameter portion 157 is set to 2.0 mm, based on these values. The area S1 of the primary flow path and the secondary flow path are obtained from the cross section (Fig. 15 (b), Fig. 15 (c)) of the heat transfer tube 11 shown in Figs. 15 (a) to 15 (c). In the area of the area S2, the ratio of the area S1 of the primary flow path to the area S2 of the secondary flow path is set to S1:S2≒1:1.47 in the large diameter portion 157, and S1:S2≒ in the small diameter portion 159. 1:1.11.

根據該傳熱構件20，對內管15中流動的熱媒進行攪拌而使其蜿 蜒，可使熱媒容易地與內管15、支撐構件19及傳熱構件20接觸。此外，通過將圓桿原材料設為以每隔規定長度而擠壓成形的形狀，而使大徑部157與支撐構件19的內徑大致相等，也使該大徑部157與支撐構件19的一部分接觸而進行支撐。 According to the heat transfer member 20, the heat medium flowing through the inner tube 15 is stirred and kneaded. That is, the heat medium can be easily brought into contact with the inner tube 15, the support member 19, and the heat transfer member 20. Further, by forming the round bar material into a shape that is extruded at a predetermined length, the large diameter portion 157 and the inner diameter of the support member 19 are substantially equal, and the large diameter portion 157 and a part of the support member 19 are also made. Support for contact.

圖16(a)是包括剖面是多邊形狀的實心桿的傳熱管的剖面圖，圖16(b)是圖16(a)的K-K剖面圖。 Fig. 16 (a) is a cross-sectional view of a heat transfer tube including a solid rod having a polygonal cross section, and Fig. 16 (b) is a cross-sectional view taken along line K-K of Fig. 16 (a).

傳熱構件20可形成為剖面是多邊形狀的實心桿165。圖例中，形成為剖面是大致三角形狀的實心桿165。實心桿165通過進行扭轉，而稜線不與軸線平行地形成為大致螺旋狀。 The heat transfer member 20 may be formed as a solid rod 165 having a polygonal cross section. In the illustrated example, a solid rod 165 having a substantially triangular cross section is formed. The solid rod 165 is twisted, and the ridge line is formed in a substantially spiral shape without being parallel to the axis.

例如，將內管15設為外徑D5=4.4 mm、內徑D6=4.0 mm，外管13設為外徑6.6 mm、內徑D4=6 mm，間隙支撐構件17設為線徑d1=0.8 mm，支撐構件19設為線徑d2=1 mm，實心桿165的剖面積設為1.8 mm2，如果根據這些數值並根據圖16(a)及圖16(b)所示的傳熱管11的剖面(圖16(b))來求出一次流路的面積S1與二次流路的面積S2的面積，則一次流路的面積S1約為9.5 mm2，二次流路的面積S2約為12.1 mm2，一次流路的面積S1與二次流路的面積S2的比約為1：1.27。 For example, the inner tube 15 is set to have an outer diameter D5 = 4.4 mm, an inner diameter D6 = 4.0 mm, an outer tube 13 is set to an outer diameter of 6.6 mm, an inner diameter D4 = 6 mm, and the gap support member 17 is set to a wire diameter d1 = 0.8. Mm, the support member 19 is set to have a wire diameter d2 = 1 mm, and the cross-sectional area of the solid rod 165 is set to 1.8 mm 2 , if according to these values and according to the heat transfer tubes 11 shown in Figs. 16(a) and 16(b) In the cross section (Fig. 16 (b)), the area S1 of the primary flow path and the area S2 of the secondary flow path are obtained, and the area S1 of the primary flow path is about 9.5 mm 2 , and the area S2 of the secondary flow path is about For 12.1 mm 2 , the ratio of the area S1 of the primary flow path to the area S2 of the secondary flow path is about 1:1.27.

根據該傳熱構件20，相比於主要僅表背面與熱媒接觸的所述帶板141，例如設為圖例的剖面三角形狀，而可使與熱媒的接觸位置為多個部位，而且稜線為大致螺旋狀，由此形成朝向支撐構件19的流動。尤其通過將剖面形狀設為星形等，且與所述同樣地以螺旋狀扭轉而形成，不會減少流路(流路剖面積)，而可進一步增大與熱媒的接觸面積。由此，可增大傳熱構件20的表面積，從而可提高熱媒與傳熱構件20的熱交換率。 According to the heat transfer member 20, the strip 141 which is mainly in contact with the heat medium only on the front and back surfaces is, for example, a cross-sectional triangular shape as shown in the drawing, and the contact position with the heat medium can be a plurality of portions, and the ridge line It is substantially spiral, thereby forming a flow toward the support member 19. In particular, by forming the cross-sectional shape into a star shape or the like and twisting it in a spiral shape in the same manner as described above, the contact area with the heat medium can be further increased without reducing the flow path (flow path sectional area). Thereby, the surface area of the heat transfer member 20 can be increased, so that the heat exchange rate between the heat medium and the heat transfer member 20 can be improved.

圖17是包括圓桿型的各所述形狀例中端部形成為流線型的傳熱構件的傳熱管的剖面圖。 Fig. 17 is a cross-sectional view showing a heat transfer tube in which an end portion of each of the shape examples of the round bar type is formed into a streamlined heat transfer member.

圓桿型的各所述形狀例的傳熱構件20優選使端部形成為流線形狀。可減少端部中流動的熱媒因來自傳熱構件20表面的漩渦等而引起的剝離或紊亂，可使熱媒的流入及流出變得順暢，且可提高熱媒與內管15內的傳熱效率。 It is preferable that the heat transfer member 20 of each of the above-described shape examples of the round bar shape has an end portion formed in a streamline shape. The peeling or turbulence caused by the vortex or the like from the surface of the heat transfer member 20 can be reduced by the heat medium flowing in the end portion, the inflow and outflow of the heat medium can be made smooth, and the heat medium and the inner tube 15 can be improved. Thermal efficiency.

本實施方式的傳熱管11以所述方式構成傳熱管列單元39，可將其作為單體熱交換器而構成，並且如圖18所示，可由多個傳熱管列單元39而構成熱交換器49。 The heat transfer tube 11 of the present embodiment constitutes the heat transfer tube array unit 39 as described above, and can be configured as a single heat exchanger, and as shown in FIG. 18, can be constituted by a plurality of heat transfer tube array units 39. Heat exchanger 49.

該熱交換器49將所述傳熱管列單元39積層多段而構成。該實施方式中積層為4段。積層配置的多個傳熱管列單元39的一次分支管21的另一端連接於一次入口集管51，二次分支管25的一端連接於二次入口集管55，一次集合管27的一端連接於一次出口集管53，二次集合管29的一端連接於二次出口集管57。積層段數並不限定於圖例的4段，可比4段少也可比4段多，優選包含4段~10段，各個集合管及分支管連接於各集管。 The heat exchanger 49 is configured by stacking the heat transfer tube row units 39 in a plurality of stages. In this embodiment, the laminate is four segments. The other end of the primary branch pipe 21 of the plurality of heat transfer tube row units 39 stacked in a stack is connected to the primary inlet header 51, and one end of the secondary branch pipe 25 is connected to the secondary inlet header 55, and one end of the primary collecting pipe 27 is connected. At one outlet header 53, one end of the secondary manifold 29 is connected to the secondary outlet header 57. The number of laminated layers is not limited to the four segments of the legend, and may be smaller than four segments or more than four segments, preferably including four segments to ten segments, and each manifold and branch pipe are connected to the respective headers.

一次入口集管51、二次入口集管55、一次出口集管53及二次出口集管57的軸線方向的一方閉合，在軸線方向的另一方固接旋入式管接頭59。雖省略圖示，但來自熱交換裝置側的一次熱媒供給配管、二次熱媒供給配管、一次熱媒環流配管及二次熱媒環流配管的管接頭包含例如使配管端部擴徑而成的喇叭部、及外插至該喇叭部的外側的帶帽螺母，在將旋入式管接頭59的前端片材面與喇叭部密接的狀態下，帶帽螺母的內螺紋與旋入式管接頭59的外螺紋擰接，由此熱交換器49裝卸自如地安裝在熱交換裝置中。這樣，經由旋入式管接頭59而相對於熱交換裝置裝卸自如地安裝熱交換器49，由此可容易地進行保養(maintenance)時的熱交換器49的更換。 One of the inlet header 51, the secondary inlet header 55, the primary outlet header 53, and the secondary outlet header 57 in the axial direction is closed, and the other in the axial direction is fixed to the screw-in fitting 59. Although not shown in the drawings, the pipe joints of the primary heat medium supply pipe, the secondary heat medium supply pipe, the primary heat medium circulation pipe, and the secondary heat medium circulating pipe from the heat exchange device side include, for example, a pipe end portion expanded. The horn portion and the cap nut that is inserted outside the horn portion, the internal thread of the cap nut and the screw-in tube are in a state in which the front end sheet surface of the screw-in fitting 59 is in close contact with the horn portion. The external thread of the joint 59 is screwed, whereby the heat exchanger 49 is detachably mounted in the heat exchange device. In this way, the heat exchanger 49 is detachably attached to the heat exchange device via the screw-in type pipe joint 59, whereby the heat exchanger 49 at the time of maintenance can be easily replaced.

一次入口集管51、二次入口集管55、一次出口集管53、及二次 出口集管57的與旋入式管接頭59的固接端相反側的端部閉合，例如利用底板61而被固定支撐著。另外，在一次入口集管51、二次入口集管55、一次出口集管53、及二次出口集管57的與旋入式管接頭59相反側的端部，也可以固接可與旋入式管接頭59擰接連接的管接頭。通過設為所述兩端接頭結構，而可將熱交換器49更多段地積層。 Primary inlet header 51, secondary inlet header 55, primary outlet header 53, and secondary The end of the outlet header 57 on the side opposite to the fixed end of the screw-in fitting 59 is closed, for example, fixedly supported by the bottom plate 61. In addition, the end portions of the primary inlet header 51, the secondary inlet header 55, the primary outlet header 53, and the secondary outlet header 57 on the opposite side of the screw-in fitting 59 may be fixed and rotatably The inlet fitting 59 is screwed to the connected fitting. The heat exchanger 49 can be laminated in more stages by setting the joint structure at both ends.

根據如所述般構成的傳熱管11，構成圖2(a)、圖2(b)、圖7(a)、圖7(b)所示的傳熱管列單元及圖18所示的熱交換器49，由此流入一次入口集管51的一次熱媒進入一次分支管21，並從一次分支管21流入至各內管15。流經內管15的一次熱媒與二次熱媒進行熱交換後，進入一次集合管27，並從一次出口集管53流向外部。流入二次入口集管55的二次熱媒進入二次分支管25，並從二次分支管25流入外管13。流經外管13的二次熱媒與一次熱媒進行熱交換後，進入二次集合管29，並從二次出口集管57流向外部。 According to the heat transfer tube 11 configured as described above, the heat transfer tube row unit shown in Figs. 2(a), 2(b), 7(a), and 7(b) and the heat transfer tube row unit shown in Fig. 18 are formed. The heat exchanger 49, whereby the primary heat medium flowing into the primary inlet header 51 enters the primary branch pipe 21, and flows into the inner pipe 15 from the primary branch pipe 21. After the primary heat medium flowing through the inner tube 15 exchanges heat with the secondary heat medium, it enters the primary collecting pipe 27 and flows from the primary outlet header 53 to the outside. The secondary heat medium flowing into the secondary inlet header 55 enters the secondary branch pipe 25 and flows into the outer pipe 13 from the secondary branch pipe 25. After the secondary heat medium flowing through the outer tube 13 exchanges heat with the primary heat medium, it enters the secondary collecting pipe 29 and flows from the secondary outlet header 57 to the outside.

對所述構成的熱交換器49的作用進行說明。 The action of the heat exchanger 49 having the above configuration will be described.

熱交換器49中，內管15中流動的熱媒一邊與設置在內管15的內側的傳熱構件20及支撐構件19接觸一邊流動，以前，僅與內管內周面38接觸的內管15內的熱媒的接觸面積增大。熱媒通過與支撐構件19、傳熱構件20進行接觸而利用熱傳遞進行熱交換。經熱交換的熱量利用熱傳導而傳遞至內管15，與流經外管13和內管15的間隙31的另一系統的熱媒進行熱交換。也就是，與傳熱構件20、支撐構件19交換的熱量有助於重新提高熱交換效率。此外，該熱交換器49中，包含外管13及內管15的多個傳熱管11相互平行地構成，且在同一平面上鄰接地排列著。該平面上構成的熱交換器49設為一個單元且可積層多段而構成，從而可在擴大傳熱面積的同時減小接地面積而構成。 In the heat exchanger (49), the heat medium flowing through the inner tube (15) flows while being in contact with the heat transfer member (20) and the support member (19) provided inside the inner tube (15), and the inner tube that is only in contact with the inner peripheral surface 38 of the inner tube. The contact area of the heat medium in 15 is increased. The heat medium exchanges heat with heat transfer by coming into contact with the support member 19 and the heat transfer member 20. The heat exchanged heat is transferred to the inner tube 15 by heat conduction, and exchanges heat with the heat medium of another system flowing through the gap 31 between the outer tube 13 and the inner tube 15. That is, the heat exchanged with the heat transfer member 20 and the support member 19 contributes to re-increasing the heat exchange efficiency. Further, in the heat exchanger 49, the plurality of heat transfer tubes 11 including the outer tube 13 and the inner tube 15 are formed in parallel with each other, and are arranged adjacent to each other on the same plane. The heat exchanger 49 formed on the plane is configured as one unit and can be formed in a plurality of stages, so that the heat transfer area can be enlarged and the ground contact area can be reduced.

此外，本實施方式的傳熱管11除所述熱交換器49外，也可構成圖19、圖20所示的圓筒狀的熱交換器65。 Further, the heat transfer tube 11 of the present embodiment may constitute the cylindrical heat exchanger 65 shown in FIGS. 19 and 20 in addition to the heat exchanger 49.

該熱交換器65是將多根該傳熱管11予以成束而構成。各傳熱管11以相互保持規定間隔的方式支撐兩端，且收容在圓筒狀的殼體67內。本實施方式中，如圖19所示，包括圓板形狀的一次隔離壁69與二次隔離壁73，該一次隔離壁69與二次隔離壁73具有矩陣狀地在縱橫方向上成為等間隔的多個內管支撐孔(一次支撐孔)71、外管支撐孔(二次支撐孔)75，利用這些一次隔離壁69、二次隔離壁73而以貫通狀態支撐兩端部分。一次隔離壁69具有設為與內管15的外徑相等的孔徑的內管支撐孔(一次支撐孔)71，且內管15貫通。二次隔離壁73具有設為與外管13相等的孔徑的外管支撐孔(二次支撐孔)75，且外管13貫通。在分別貫通的狀態下，在一次隔離壁69與殼體67的端部壁77之間，在內管15的入口端側形成著一次分支部79，在內管15的出口端側形成著一次集合部81。此外，在一次隔離壁69與二次隔離壁73之間，在外管13的入口端側形成著二次分支部83，在外管13的出口端側形成著二次集合部85。另外，這些傳熱管11的外管13及內管15與各一次隔離壁69、二次隔離壁73的連接也是利用所述焊接來進行，就與配置於外管13與內管15的間隙的間隙支撐構件17的固定而言也同樣，且外管13、內管15的端部在各一次隔離壁69、二次隔離壁73的外側開口。 The heat exchanger (65) is configured by bundles a plurality of the heat transfer tubes (11). Each of the heat transfer tubes 11 supports both ends so as to maintain a predetermined interval therebetween, and is housed in a cylindrical casing 67. In the present embodiment, as shown in FIG. 19, a primary partitioning wall 69 and a secondary partitioning wall 73 having a circular plate shape are formed, and the primary partitioning wall 69 and the secondary partitioning wall 73 have a matrix shape and are equally spaced in the longitudinal and lateral directions. A plurality of inner tube support holes (primary support holes) 71 and outer tube support holes (secondary support holes) 75 support the both end portions in a penetrating state by the primary partition walls 69 and the secondary partition walls 73. The primary partition wall 69 has an inner tube support hole (primary support hole) 71 that is equal to the outer diameter of the inner tube 15, and the inner tube 15 penetrates. The secondary partition wall 73 has an outer tube support hole (secondary support hole) 75 that is equal in diameter to the outer tube 13, and the outer tube 13 penetrates. In a state of being respectively penetrated, between the primary partition 69 and the end wall 77 of the casing 67, a branch portion 79 is formed on the inlet end side of the inner tube 15, and the outlet end side of the inner tube 15 is formed once. The collection unit 81. Further, between the primary partition wall 69 and the secondary partition wall 73, a secondary branch portion 83 is formed on the inlet end side of the outer tube 13, and a secondary aggregate portion 85 is formed on the outlet end side of the outer tube 13. Further, the connection between the outer tube 13 and the inner tube 15 of the heat transfer tubes 11 and the primary partition walls 69 and the secondary partition walls 73 is also performed by the welding, and is disposed in the gap between the outer tube 13 and the inner tube 15. The same applies to the fixing of the gap support member 17, and the ends of the outer tube 13 and the inner tube 15 are opened outside the primary partition wall 69 and the secondary partition wall 73.

在殼體67內的兩個二次隔離壁73、二次隔離壁73之間設置著多個整流板87。這些整流板87形成與傳熱管11的長度方向正交的面，並且設為分別在殼體67內具有一部分不與殼體67的內周面接觸的切口狀的通過部89的形狀，例如設為大致半月板(Meniscus)形狀。這些整流板87的通過部89以在殼體67內的軸線方向上交替地定位的方式而設置，由此 在殼體67內形成Z字形蜿蜒的三次流路。另外，各整流板87中包括貫通孔，該貫通孔供各傳熱管11貫通且可支撐這些傳熱管11，對於這些貫通孔與各傳熱管11的外管13而言，也優選進行與所述同樣的焊接固定。 A plurality of rectifying plates 87 are disposed between the two secondary partition walls 73 and the secondary partition walls 73 in the casing 67. These rectifying plates 87 have a surface orthogonal to the longitudinal direction of the heat transfer tube 11, and have a shape of a slit-shaped passage portion 89 that does not partially contact the inner peripheral surface of the casing 67 in the casing 67, for example, for example. Set to roughly the shape of the Meniscus. The passage portions 89 of the flow regulating plates 87 are disposed alternately in the axial direction in the casing 67, thereby A three-way flow path of a zigzag shape is formed in the casing 67. Further, each of the rectifying plates 87 includes a through hole through which the heat transfer tubes 11 pass and can support the heat transfer tubes 11, and it is preferable that the through holes and the outer tubes 13 of the heat transfer tubes 11 are also preferably performed. It is fixed by the same welding as described.

此外，如圖20所示，在殼體67的一端側，在一次分支部79配設著一次入口集管91，在二次集合部85配設著二次出口集管93，並且配設著成為三次流路的入口的三次入口集管95。此外，在殼體67的另一端側，在一次集合部81配設著一次出口集管97，在二次分支部83配設著二次入口集管99，並且配設著成為三次流路的出口的三次出口集管101。 Further, as shown in FIG. 20, on one end side of the casing 67, a primary inlet header 91 is disposed in the primary branch portion 79, and a secondary outlet header 93 is disposed in the secondary assembly portion 85, and is disposed Three inlet headers 95 that become the inlets of the three flow paths. Further, on the other end side of the casing 67, a primary outlet header 97 is disposed in the primary collecting portion 81, a secondary inlet header 99 is disposed in the secondary branching portion 83, and a tertiary flow path is disposed. Three outlet headers 101 for the outlet.

根據如此構成的熱交換器65，流入一次入口集管91的一次熱媒進入一次分支部79，並從一次分支部79流入各內管15。內管15內流動的一次熱媒在與二次熱媒進行熱交換後，進入一次集合部81，並從一次出口集管97流向外部。流入二次入口集管99的二次熱媒進入二次分支部83，並從二次分支部83流向外管13。流經外管13的二次熱媒在與一次熱媒進行熱交換後，進入二次集合部85，並從二次出口集管93流向外部。流入三次入口集管95的三次熱媒進入殼體67，且利用各整流板87蜿蜒而沿外管13的周圍流動。殼體67內流動的三次熱媒在與二次熱媒進行熱交換後，從三次出口集管101流向外部。另外，三次熱媒也可與一次熱媒相同。 According to the heat exchanger 65 configured as described above, the primary heat medium that has flowed into the primary inlet header 91 enters the primary branch portion 79, and flows into the inner tube 15 from the primary branch portion 79. The primary heat medium flowing in the inner tube 15 exchanges heat with the secondary heat medium, enters the primary collecting portion 81, and flows from the primary outlet header 97 to the outside. The secondary heat medium flowing into the secondary inlet header 99 enters the secondary branch portion 83 and flows from the secondary branch portion 83 to the outer tube 13. After the secondary heat medium flowing through the outer tube 13 exchanges heat with the primary heat medium, it enters the secondary collecting portion 85 and flows from the secondary outlet header 93 to the outside. The three heat medium flowing into the three inlet headers 95 enters the casing 67, and flows around the outer pipe 13 by the respective rectifying plates 87. The tertiary heat medium flowing in the casing 67 is subjected to heat exchange with the secondary heat medium, and then flows from the tertiary outlet header 101 to the outside. In addition, the tertiary heat medium can also be the same as the primary heat medium.

在該熱交換器65中，傳熱管11與殼體67內的三次熱媒進行熱交換，因而所述內管15內的一次流路的面積S1與外管13內的二次流路的面積S2的比S1：S2可設定為1：4~1：2，關於位於外管13與內管15的間隙部分的間隙支撐構件17或內管15內的支撐構件19的線徑、傳熱構件20的形狀、剖面積等，也可根據一次流路的面積S1與二次流路的面積S2的比而適當地增減。 In the heat exchanger 65, the heat transfer tube 11 exchanges heat with the tertiary heat medium in the casing 67, so that the area S1 of the primary flow path in the inner tube 15 and the secondary flow path in the outer tube 13 The ratio S1:S2 of the area S2 can be set to 1:4 to 1:2, and the wire diameter and heat transfer of the support member 17 in the gap support member 17 or the inner tube 15 located in the gap portion between the outer tube 13 and the inner tube 15 The shape, sectional area, and the like of the member 20 may be appropriately increased or decreased according to the ratio of the area S1 of the primary flow path to the area S2 of the secondary flow path.

因此，根據本實施方式的傳熱管11及熱交換器49，可提高內管 15及該內管15中流動的熱媒的熱交換效率。 Therefore, according to the heat transfer tube 11 and the heat exchanger 49 of the present embodiment, the inner tube can be improved 15 and the heat exchange efficiency of the heat medium flowing in the inner tube 15.

11‧‧‧傳熱管 11‧‧‧ heat transfer tube

13‧‧‧外管 13‧‧‧External management

15‧‧‧內管 15‧‧‧Inside

17‧‧‧間隙支撐構件 17‧‧‧Gap support members

19‧‧‧支撐構件 19‧‧‧Support members

31‧‧‧間隙 31‧‧‧ gap

d1、d2‧‧‧線徑 D1, d2‧‧‧ wire diameter

D1‧‧‧捲內徑 D1‧‧‧ roll inner diameter

D2、D3‧‧‧捲外徑 D2, D3‧‧ vol.

D4、D6‧‧‧內徑 D4, D6‧‧‧ inside diameter

D5‧‧‧外徑 D5‧‧‧ OD

S1‧‧‧一次流路的面積 S1‧‧‧ area of a flow path

S2‧‧‧二次流路的面積 S2‧‧‧ area of secondary flow path

W‧‧‧間隙長度(間隙幅長) W‧‧‧ gap length (length gap)

Claims (11)

一種傳熱管，其特徵在於包括：外管；內管，***至所述外管；間隙支撐構件，配置在所述外管的內周面與所述內管的外周面的間隙內，且包含遍及所述外管的全長而螺旋狀地與所述外管的內周面及所述內管的外周面接觸的線材；以及支撐構件，包含遍及所述內管的全長而螺旋狀地與所述內管的內周面接觸的線材。 A heat transfer tube, comprising: an outer tube; an inner tube inserted into the outer tube; and a gap support member disposed in a gap between an inner circumferential surface of the outer tube and an outer circumferential surface of the inner tube, and a wire member that is spirally connected to an inner circumferential surface of the outer tube and an outer circumferential surface of the inner tube over the entire length of the outer tube; and a support member that spirally extends over the entire length of the inner tube a wire that is in contact with the inner peripheral surface of the inner tube. 如申請專利範圍第1項所述的傳熱管，其中所述間隙支撐構件包含捲材，且線徑設為與所述間隙相等。 The heat transfer tube according to claim 1, wherein the gap supporting member comprises a coil, and a wire diameter is set equal to the gap. 如申請專利範圍第1項所述的傳熱管，其中所述間隙支撐構件包含小徑部與大徑部交替地形成的捲材，線徑比所述間隙小，所述小徑部的捲內徑設為所述內管的外徑，所述大徑部的捲外徑設為所述外管的內徑，且所述內管支撐於所述外管內。 The heat transfer tube according to the first aspect of the invention, wherein the gap support member comprises a coil material formed by alternately forming a small diameter portion and a large diameter portion, wherein a wire diameter is smaller than the gap, and the small diameter portion is rolled. The inner diameter is set to an outer diameter of the inner tube, the outer diameter of the large diameter portion is set to an inner diameter of the outer tube, and the inner tube is supported in the outer tube. 一種傳熱管，其特徵在於包括：外管；內管，***至所述外管；間隙支撐構件，配置在外管內周面與內管外周面的間隙內，且包含遍及所述外管的全長而螺旋狀地與所述外管內周面及所述內管外周面接觸的線材；支撐構件，包含遍及所述內管的全長而螺旋狀地與內管內周面接觸的線材；以及傳熱構件，遍及所述支撐構件的全長而設置在所述支撐構件的中心， 且至少外周的一部分與所述支撐構件接觸。 A heat transfer tube, comprising: an outer tube; an inner tube inserted into the outer tube; and a gap supporting member disposed in a gap between an inner circumferential surface of the outer tube and an outer circumferential surface of the inner tube, and including the outer tube a wire member that is spirally connected to the inner circumferential surface of the outer tube and the outer circumferential surface of the inner tube; the support member includes a wire material that spirally contacts the inner circumferential surface of the inner tube over the entire length of the inner tube; a heat transfer member disposed at a center of the support member throughout a total length of the support member And at least a portion of the outer circumference is in contact with the support member. 如申請專利範圍第4項所述的傳熱管，其中所述傳熱構件為在所述支撐構件的長度方向上是長的且螺旋狀地扭轉的帶板。 The heat transfer tube according to claim 4, wherein the heat transfer member is a strip that is long and spirally twisted in the longitudinal direction of the support member. 如申請專利範圍第4項所述的傳熱管，其中所述傳熱構件為外周部凸出圓桿，所述外周部凸出圓桿具有在所述支撐構件的長度方向上每隔規定間隔擠壓圓形外周而變形的長圓部。 The heat transfer tube according to claim 4, wherein the heat transfer member is an outer peripheral protruding round bar, and the outer peripheral protruding round bar has a predetermined interval in a longitudinal direction of the support member. An oblong portion that is deformed by pressing a circular outer circumference. 如申請專利範圍第4項所述的傳熱管，其中所述傳熱構件為異徑圓桿，所述異徑圓桿是在所述支撐構件的長度方向上每隔規定間隔使圓形外周由小徑部與大徑部交替形成。 The heat transfer tube according to Item 4, wherein the heat transfer member is a reducer round rod, and the reducer round rod is a circular outer circumference at regular intervals in a longitudinal direction of the support member. The small diameter portion and the large diameter portion are alternately formed. 如申請專利範圍第4項所述的傳熱管，其中所述傳熱構件為剖面是多邊形狀的實心桿。 The heat transfer tube according to claim 4, wherein the heat transfer member is a solid rod having a polygonal cross section. 一種熱交換器，其特徵在於：使用如申請專利範圍第1項至第8項中任一項所述的傳熱管，所述傳熱管相互平行而配置著多個；將所有內管入口端連接於一次分支管且將所有內管出口端連接於一次集合管而構成一次流路，並且將所有外管入口端連接於二次分支管且將所有外管出口端連接於二次集合管而構成二次流路。 A heat exchanger according to any one of claims 1 to 8, wherein the heat transfer tubes are arranged in parallel with each other; The end is connected to the primary branch pipe and connects all the inner pipe outlet ends to the primary collecting pipe to form a primary flow path, and connects all the outer pipe inlet ends to the secondary branch pipe and connects all the outer pipe outlet ends to the secondary collecting pipe And constitute a secondary flow path. 一種熱交換器，其特徵在於：使用如申請專利範圍第1項至第8項中任一項所述的傳熱管，將多根所述傳熱管予以成束，將所述傳熱管的束收容在圓筒形狀的殼體內，將所述內管的入口端彼此及出口端彼此分別連接而構成一次流路，並且將所述外管的入口端彼此及出口端彼此分別連接而構成二次流路，且 在所述殼體內作為三次流路而構成。 A heat exchanger characterized by using a heat transfer tube according to any one of claims 1 to 8 to bundle a plurality of the heat transfer tubes, the heat transfer tubes The bundle is housed in a cylindrical casing, and the inlet ends of the inner tubes and the outlet ends are connected to each other to form a primary flow path, and the inlet ends and the outlet ends of the outer tubes are respectively connected to each other to constitute a bundle. Secondary flow path, and It is constituted as a tertiary flow path in the casing. 如申請專利範圍第10項所述的熱交換器，其中在所述殼體內設置著多個整流板，所述整流板具有與所述傳熱管的長度方向正交的面，對各所述傳熱管進行支撐並且使所述三次流路蜿蜒。 The heat exchanger according to claim 10, wherein a plurality of rectifying plates are disposed in the casing, the rectifying plate having a face orthogonal to a longitudinal direction of the heat transfer pipe, for each of the The heat transfer tubes are supported and the three flow paths are collapsed.
TW102111910A 2012-04-05 2013-04-02 Heat transfer pipe and heat exchanger using the same TW201346206A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2012086562 2012-04-05
JP2012169987 2012-07-31

Publications (1)

Publication Number Publication Date
TW201346206A true TW201346206A (en) 2013-11-16

Family

ID=49300319

Family Applications (1)

Application Number Title Priority Date Filing Date
TW102111910A TW201346206A (en) 2012-04-05 2013-04-02 Heat transfer pipe and heat exchanger using the same

Country Status (6)

Country Link
US (1) US20150300746A1 (en)
JP (1) JPWO2013150818A1 (en)
KR (1) KR20150006823A (en)
CN (2) CN203323601U (en)
TW (1) TW201346206A (en)
WO (1) WO2013150818A1 (en)

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20150006823A (en) * 2012-04-05 2015-01-19 씨. 아이. 카세이 가부시기가이샤 Heat transfer tube, and heat exchanger using same
JP2015135210A (en) * 2014-01-17 2015-07-27 シーアイ化成株式会社 Heat transfer tube for heat exchanger and heat exchanger
CN105333613B (en) * 2014-08-15 2019-05-14 长沙英芙机电科技有限公司 A kind of water heater and condenser
PL409856A1 (en) * 2014-10-20 2015-06-08 Feerum Spółka Akcyjna Tubular heat exchanger of the gas-gas type
CN104482650A (en) * 2014-12-24 2015-04-01 武汉浩宏科技有限公司 Air energy water heater and condenser thereof
CN104501479A (en) * 2014-12-24 2015-04-08 武汉浩宏科技有限公司 Double-spiral type condenser and air-source water heater comprising same
EP3128278B1 (en) * 2015-08-06 2018-06-20 Linde Aktiengesellschaft Feeding and removal of pipe streams with interim temperature in coiled heat exchangers
US10429084B2 (en) 2017-02-21 2019-10-01 A. O. Smith Corporation Heat pump water heater
CN106855367B (en) * 2017-02-28 2024-01-26 郑州大学 Shell-and-tube heat exchanger with distributed inlets and outlets
CN106679467B (en) * 2017-02-28 2019-04-05 郑州大学 Shell-and-tube heat exchanger with external bobbin carriage
CN106895714A (en) * 2017-04-11 2017-06-27 成都市双流壁挂热交换器有限责任公司 Bilateral channel heat exchanger
AT519546B1 (en) * 2017-04-12 2018-08-15 Brandstetter Johann heat exchangers
CN107238308A (en) * 2017-07-25 2017-10-10 陕西路圣里德太阳能研究院有限公司 Heat conduction profit finned tube set of heat exchange tubes and energy storage device
KR102482259B1 (en) * 2017-10-27 2022-12-27 차이나 페트로리움 앤드 케미컬 코포레이션 Improved heat transfer pipe, and pyrolysis furnace including the same
WO2019177209A1 (en) * 2018-03-14 2019-09-19 주식회사 에너솔라 Heat exchange device and heat pump sequential control apparatus having same
JP2019190787A (en) * 2018-04-27 2019-10-31 株式会社デンソー Heat exchanger
CN108981430A (en) * 2018-09-25 2018-12-11 江西中医药大学 A kind of double pipe heat exchanger and heat-exchange system
CN114728261A (en) * 2019-12-20 2022-07-08 M技术株式会社 Flow reactor
KR102513327B1 (en) * 2020-12-16 2023-03-23 재단법인 포항산업과학연구원 Gas-gas tube heat exchanger including insert with irregular pitch
CN118031684B (en) * 2024-04-15 2024-06-11 江苏曙光压力容器有限公司 Heat exchanger with self-cleaning function

Family Cites Families (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3151672A (en) * 1961-10-30 1964-10-06 Westinghouse Air Brake Co Water cooled air cooler
BE795314A (en) * 1972-02-10 1973-05-29 Raufoss Ammunisjonsfabrikker HEAT EXCHANGER DUCT
US4443389A (en) * 1981-04-27 1984-04-17 Leonard Oboler Heat exchange apparatus
US4798241A (en) * 1983-04-04 1989-01-17 Modine Manufacturing Mixed helix turbulator for heat exchangers
JPS59158888U (en) * 1983-04-08 1984-10-24 石川島播磨重工業株式会社 Heat exchanger
JPS60114603A (en) * 1983-11-25 1985-06-21 株式会社日本ケミカル・プラント・コンサルタント Evaporator
SE457330B (en) * 1987-10-20 1988-12-19 Tilly S Roer Ab DEVICE FOR TEMPERATURE AND HOMOGENIZATION OF TRUE FLUID MASSES
US4794980A (en) * 1987-11-16 1989-01-03 Raydot Incorporated Air to air heat exchanger
US5167275A (en) * 1989-12-06 1992-12-01 Stokes Bennie J Heat exchanger tube with turbulator
US5497824A (en) * 1990-01-18 1996-03-12 Rouf; Mohammad A. Method of improved heat transfer
JP2734893B2 (en) * 1992-07-31 1998-04-02 ダイキン工業株式会社 Cryogenic refrigerator
JPH07218159A (en) * 1994-01-31 1995-08-18 Sanyo Electric Co Ltd Heat exchanger
FR2788590B1 (en) * 1999-01-14 2001-06-08 Sirven HEAT EXCHANGER, ESPECIALLY FOR MANURE PREHEATING
US6675746B2 (en) * 1999-12-01 2004-01-13 Advanced Mechanical Technology, Inc. Heat exchanger with internal pin elements
JP2001201275A (en) * 2000-01-21 2001-07-27 Daikin Ind Ltd Double tube heat exchanger
KR100419065B1 (en) * 2001-03-07 2004-02-19 주식회사 엘지화학 Pyrolysis Tube and Pyrolysis Method for using the same
JP3558131B2 (en) * 2002-04-17 2004-08-25 松本重工業株式会社 Double tube heat exchanger
JP2005127684A (en) * 2003-10-27 2005-05-19 Atago Seisakusho:Kk Double tube type heat exchanger
US20050150640A1 (en) * 2004-01-09 2005-07-14 Ranga Nadig Double-tube apparatus for use in a heat exchanger and method of using the same
JP2006234355A (en) * 2005-02-28 2006-09-07 Matsushita Electric Ind Co Ltd Heat exchanger
JP2007093082A (en) * 2005-09-28 2007-04-12 Matsushita Electric Ind Co Ltd Heat exchanger
US9587888B2 (en) * 2008-07-24 2017-03-07 Mahle International Gmbh Internal heat exchanger assembly
US8606138B2 (en) * 2009-08-05 2013-12-10 Ricoh Company, Limited Cooling device having a turbulence generating unit
JP2012007773A (en) * 2010-06-23 2012-01-12 Panasonic Corp Heat exchanger
JP5743051B2 (en) * 2010-09-15 2015-07-01 三浦工業株式会社 Heat exchanger and boiler water supply system
KR20150006823A (en) * 2012-04-05 2015-01-19 씨. 아이. 카세이 가부시기가이샤 Heat transfer tube, and heat exchanger using same

Also Published As

Publication number Publication date
CN103363820A (en) 2013-10-23
US20150300746A1 (en) 2015-10-22
CN203323601U (en) 2013-12-04
JPWO2013150818A1 (en) 2015-12-17
WO2013150818A1 (en) 2013-10-10
KR20150006823A (en) 2015-01-19

Similar Documents

Publication Publication Date Title
TW201346206A (en) Heat transfer pipe and heat exchanger using the same
US11796256B2 (en) Spiral tube heat exchanger
US7322404B2 (en) Helical coil-on-tube heat exchanger
US20160018168A1 (en) Angled Tube Fins to Support Shell Side Flow
US10041740B2 (en) Heat exchanger and production method therefor
JP2002228370A (en) Heat exchanger
JP2016102643A (en) Heat exchanger
JP2005127684A (en) Double tube type heat exchanger
JPH1038491A (en) Double tube type heat exchanger
EP3676539B1 (en) Heat exchanger for a boiler, and heat-exchanger tube
RU2382973C1 (en) Single-flow tubular coil
CN110567298A (en) Nested formula spiral baffling board and heat exchanger
CN204665975U (en) Multimedium is around heat exchange of heat pipe
CN109506497A (en) A kind of high-efficiency compact capillary heat exchange of heat pipe
CN104819652B (en) Multimedium is around heat exchange of heat pipe
KR20110083019A (en) Connector for double-pipe heat exchanger and heat exchanger having the same
RU62694U1 (en) HEAT EXCHANGE ELEMENT
WO2015107970A1 (en) Heat transfer tube for heat exchanger and heat exchanger
KR101837087B1 (en) Curved surface micro-channel heat exchanger and the method of manufacturing the same
CN210346441U (en) Coil pipe for heat exchanger
KR20150004531A (en) Heat Exchanger
RU2739962C2 (en) Radial-tube cross flow heat-mass exchange apparatus
JP6254364B2 (en) Heat exchanger for heat pump water heater
JP2002333289A (en) Heat exchanger
JP2015102265A (en) Heat transfer tube for heat exchanger