JP2006071270A - Heat exchanger, intermediate heat exchanger, and refrigeration cycle - Google Patents

Heat exchanger, intermediate heat exchanger, and refrigeration cycle Download PDF

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Publication number
JP2006071270A
JP2006071270A JP2005224926A JP2005224926A JP2006071270A JP 2006071270 A JP2006071270 A JP 2006071270A JP 2005224926 A JP2005224926 A JP 2005224926A JP 2005224926 A JP2005224926 A JP 2005224926A JP 2006071270 A JP2006071270 A JP 2006071270A
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Prior art keywords
heat exchanger
refrigerant
inner tube
heat exchange
pressure refrigerant
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JP2005224926A
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Japanese (ja)
Inventor
Shigeji Ichiyanagi
Koichiro Take
茂治 一柳
幸一郎 武
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Showa Denko Kk
昭和電工株式会社
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Application filed by Showa Denko Kk, 昭和電工株式会社 filed Critical Showa Denko Kk
Priority to JP2005224926A priority patent/JP2006071270A/en
Publication of JP2006071270A publication Critical patent/JP2006071270A/en
Pending legal-status Critical Current

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B40/00Subcoolers, desuperheaters or superheaters
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10Heat-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
    • F28D7/106Heat-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00Tubular elements; Assemblies of tubular elements
    • F28F1/10Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/42Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00Tubular elements; Assemblies of tubular elements
    • F28F1/10Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/42Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/422Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element with outside means integral with the tubular element and inside means integral with the tubular element
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2309/00Gas cycle refrigeration machines
    • F25B2309/06Compression machines, plant or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061Compression machines, plant or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure

Abstract

The present invention provides a heat exchanger that can improve heat exchange performance and has excellent bending workability.
In the present invention, an inner tube having a plurality of fins on the outer periphery is inserted and arranged in an outer tube, and a first fluid flowing through the inner tube is connected between the tubes. It is intended for a heat exchanger that allows heat exchange with a second fluid that circulates. A gap S is formed between the inner peripheral surface of the outer tube 30 and the tips of the fins 21 in the inner tube 20.
[Selection] Figure 2

Description

  The present invention relates to a refrigeration cycle employed in, for example, a car air conditioner refrigeration system, and an intermediate heat exchanger and a heat exchanger used in the cycle.

Conventionally, in the vapor compression refrigeration cycle, a chlorofluorocarbon-based refrigerant has been used in many cases. However, in recent years, from the viewpoint of protecting the global environment, a refrigeration cycle in which a natural refrigerant such as carbon dioxide (CO 2 ) is used. Is attracting attention.

  In such a refrigeration cycle, the high-pressure refrigerant that has passed through the compressor and gas cooler (condenser) is circulated back to the compressor as low-pressure refrigerant through the decompressor and evaporator. In order to improve performance, a technique for exchanging heat between a high-pressure refrigerant and a low-pressure refrigerant using an intermediate heat exchanger has been proposed.

As the intermediate heat exchanger for the CO 2 refrigeration cycle, for example, those having a tube structure described in Patent Documents 1 to 3 below are well known.

  The heat exchangers shown in Patent Literatures 1 and 2 are configured with a tube member having a porous structure, and are provided with a central flow path along an axis and a plurality of peripheral flow paths on the outer periphery. The high-pressure refrigerant is circulated through the central flow path, and the low-pressure refrigerant is circulated through the outer peripheral flow path so that heat is exchanged between the two refrigerants.

In the heat exchanger shown in Patent Document 3, an inner tube having a plurality of fins on the outer periphery is inserted into the outer tube, and a high-pressure refrigerant is circulated in the inner tube, and between the two tubes. A low-pressure refrigerant is circulated to exchange heat between the two refrigerants.
Japanese Patent Laid-Open No. 2001-56188 (FIG. 5) JP 2002-181466 (FIG. 3) International Publication No. WO03 / 085344 (Figure 1-2)

  However, although the heat exchangers shown in Patent Documents 1 and 2 are usually formed integrally by extrusion, it is difficult to form a heat exchanger tube having a large number of flow holes by extrusion, For example, the diameter and shape of the flow hole are restricted. For this reason, the hole diameter of the flow holes cannot be increased, the flow resistance increases, the thickness of the partition walls (fins) between the flow holes also increases, the heat transfer performance decreases, and the heat exchange performance decreases. There was a problem that. Furthermore, since the entire tube is formed by an integrally molded product and the partition walls (fins) between the flow holes are thick, bending is difficult. For example, when it is used in a refrigeration cycle for a car air conditioner, it is limited in the automobile. In addition, there is a problem that the shape in the installation space cannot be processed and the degree of freedom in design is reduced.

  Further, in the heat exchanger shown in Patent Document 3, since the inner tube is restrained by the outer tube, for example, an external force applied to the outer tube is likely to affect the inner tube, and when bent, a fin on the outer side of the inner tube is bent. As described above, there is a problem that bending work is difficult, such as cracks occurring in the film and pressure resistance and durability being lowered.

  An object of the present invention is to provide a heat exchanger, an intermediate heat exchanger, and a refrigeration cycle that can solve the above-described problems of the prior art, improve heat exchange performance, and have excellent bending workability.

  In order to achieve the above object, the present invention has the following structure.

[1] An inner tube (inner tube) provided with a plurality of fins on the outer periphery is inserted and arranged in an outer tube (outer tube), and a first fluid that circulates in the inner tube and a first fluid that circulates between both tubes. A heat exchanger configured to exchange heat between two fluids,
A heat exchanger, wherein a gap is formed between the inner peripheral surface of the outer tube and the tip of the fin.

  [2] The heat exchanger according to the above item 1, wherein the plurality of fins are arranged along the length direction of the inner tube and arranged at intervals in the circumferential direction.

  [3] The heat exchanger according to item 1 or 2, wherein a gap between the inner peripheral surface of the outer tube and the tip of the fin is set to 0.2 to 1 mm.

  [4] The heat exchanger according to any one of items 1 to 3, wherein 13 to 18 fins are formed in a circumferential direction.

  [5] The heat exchanger according to any one of items 1 to 4, wherein the fin has a thickness set to 0.3 to 1.3 mm.

  [6] The heat exchanger according to any one of the preceding items 1 to 5, wherein an opening angle in a circumferential direction between adjacent fins is set to 15 to 30 °.

  [7] The heat exchanger according to any one of items 1 to 6, wherein the fin is formed integrally with the inner tube.

  [8] The heat exchanger according to any one of 1 to 7 above, wherein both the tubes are bent.

  [9] The heat exchanger according to any one of items 1 to 8, wherein the first fluid is configured by a high-pressure heat medium, and the second fluid is configured by a low-pressure heat medium.

  [10] The heat exchanger according to any one of items 1 to 9, wherein an inner fin is provided on an inner peripheral surface of the inner tube.

[11] Among the refrigerants circulating in the refrigeration cycle, an intermediate heat exchanger configured to exchange heat between the high-pressure refrigerant and the low-pressure refrigerant,
An inner tube provided with a plurality of fins on the outer periphery;
In an aspect in which a gap is formed between an inner peripheral surface and the tip of the fin, an outer tube into which the inner tube is inserted and disposed,
One of the high-pressure refrigerant and the low-pressure refrigerant is circulated through the first heat exchange path in the inner tube, and the other refrigerant is circulated through the second heat exchange path between the tubes. Intermediate heat exchanger.

  [12] The intermediate heat exchanger according to [11], wherein high-pressure refrigerant is circulated through the first heat exchange path and low-pressure refrigerant is circulated through the second heat exchange path.

  [13] The intermediate heat exchanger according to the above item 11 or 12, wherein the refrigerant is composed of a carbon dioxide refrigerant.

[14] An intermediate heat exchanger configured to exchange heat between a high-temperature refrigerant and a low-temperature refrigerant among refrigerants circulating in the refrigeration cycle,
An inner tube provided with a plurality of fins on the outer periphery;
In an aspect in which a gap is formed between an inner peripheral surface and the fin, the outer tube is provided with the inner tube inserted and arranged,
One of the high-temperature refrigerant and the low-temperature refrigerant is circulated through the first heat exchange path in the inner tube, and the other refrigerant is circulated through the second heat exchange path between the tubes. Intermediate heat exchanger.

[15] A refrigeration cycle in which the refrigerant circulates back through the compressor, condenser, decompressor and evaporator back to the compressor,
An intermediate heat exchanger for exchanging heat between the high-pressure refrigerant flowing through the high-pressure circuit from the compressor to the decompressor and the low-pressure refrigerant flowing through the low-pressure circuit from the decompressor to the compressor;
The intermediate heat exchanger is
An inner tube provided with a plurality of fins on the outer periphery;
In an aspect in which a gap is formed between an inner peripheral surface and the tip of the fin, an outer tube into which the inner tube is inserted and arranged,
One of the high-pressure refrigerant and the low-pressure refrigerant is circulated through the first heat exchange path in the inner tube, and the other refrigerant is circulated through the second heat exchange path between the tubes. Refrigeration cycle to be.

[16] A refrigeration cycle in which refrigerant circulates back through the compressor, condenser, decompressor and evaporator back to the compressor,
An intermediate heat exchanger for exchanging heat between the high-pressure refrigerant flowing between the condenser and the decompressor and the low-pressure refrigerant flowing between the evaporator and the compressor;
The intermediate heat exchanger is
An inner tube provided with a plurality of fins on the outer periphery;
In an aspect in which a gap is formed between an inner peripheral surface and the tip of the fin, an outer tube into which the inner tube is inserted and arranged,
One of the high-pressure refrigerant and the low-pressure refrigerant is circulated through the first heat exchange path in the inner tube, and the other refrigerant is circulated through the second heat exchange path between the tubes. Refrigeration cycle to be.

  [17] The refrigeration cycle according to item 16, wherein the high-pressure refrigerant is circulated through the first heat exchange path and the low-pressure refrigerant is circulated through the second heat exchange path.

  [18] The refrigeration cycle according to the above item 16 or 17, wherein the condenser is configured by a gas cooler.

  [19] The refrigeration cycle according to any one of [16] to [18], wherein the refrigerant is composed of a carbon dioxide refrigerant.

  [20] The refrigeration cycle according to any one of items 16 to 19, wherein both tubes as the intermediate heat exchanger are bent.

  According to the invention of [1], since it can be formed by combining a finned inner tube and an outer tube, for example, compared to the case of forming a heat exchanger porous tube by a single extrusion, a fin or tube The wall and the like can be formed thin and can be formed in a dense structure, and the heat exchange performance can be improved.

  Furthermore, since a gap is formed between the fin tip of the inner tube and the inner peripheral surface of the outer tube, the inner tube is not excessively restrained by the outer tube, and the inner tube is subjected to stress during bending. Problems such as damage to the fins can be prevented. Therefore, it can be accurately bent into a desired shape and has excellent bending workability.

  Moreover, since the clearance gap is formed in the fin front-end | tip, when the 2nd fluid mixes through the clearance gap, the bias of temperature distribution can be prevented and heat exchange efficiency can be improved further.

  According to the invention [2], the heat exchange efficiency can be improved.

  According to the invention of [3], better bending workability can be obtained.

  According to the inventions [4] to [6], the heat exchange efficiency can be further improved.

  According to the inventions [7] to [10], the above effects can be obtained more reliably.

  According to the inventions [11] to [14], an intermediate heat exchanger having the same effects as described above can be provided.

  According to the inventions [15] to [20], a refrigeration cycle having the same effect as described above can be provided.

  FIG. 1 is a refrigerant circuit diagram showing a refrigeration cycle for a car air conditioner in which a heat exchanger according to an embodiment of the present invention is employed. As shown in the figure, this refrigeration cycle uses carbon dioxide refrigerant as a refrigerant, and is a decompressor such as a compressor (1), a gas cooler (condenser 2), and an expansion valve (3). And an evaporator (4) and an intermediate heat exchanger (10), which will be described in detail later. The refrigerant compressed by the compressor (1) is cooled by the gas cooler (2) and is further expanded by an expansion valve ( The pressure is reduced by 3). Further, a refrigerant circulation path is formed in which the refrigerant is evaporated by the evaporator (4) and then returned to the compressor (1). Further, high-pressure refrigerant (outward refrigerant) from the gas cooler (2) toward the expansion valve (3) is circulated through the high-pressure refrigerant heat exchange path (25) of the intermediate heat exchanger (10) and the evaporator (4). The low-pressure refrigerant (return refrigerant) heading from the compressor to the compressor (1) is circulated through the low-pressure refrigerant heat exchange path (35) of the intermediate heat exchanger (10) to exchange heat between the two refrigerants. Yes.

  As shown in FIG. 2, the intermediate heat exchanger (10) has a double-pipe structure, and an inner tube (20) made of an extruded product of aluminum (including its alloy), as well as an aluminum extrusion. And an outer tube (30) made of a molded product.

  The inner tube (20) is integrally formed with a plurality of fins (21) on the outer periphery. The fins (21) extend continuously in the tube length direction and are provided at equal intervals in the circumferential direction. In the inner tube (20), a plurality of inner fins (22) are integrally formed at a predetermined interval in the circumferential direction and extending continuously in the tube length direction.

  The outer tube (30) is formed such that the inner diameter of the tube hole is larger than the outer diameter including the fin (21) of the inner tube (20), and the inner tube (20) has the axial center aligned in the tube hole. It is inserted and arranged in this way. A first heat exchange path (25) through which the high-pressure refrigerant (first fluid) flows is formed inside the inner tube (20), and a low-pressure refrigerant is formed between the inner tube (20) and the outer tube (30). A second heat exchange path (35) through which (second fluid) flows is formed.

  Here, in the present embodiment, the inner tube (20) is disposed so that a gap (S) is formed between the tip of the fin (21) and the inner peripheral surface of the outer tube (30). 20) is configured not to be restrained by the outer tube (30).

  Specifically, the dimension (Ls) of the gap (S) is preferably adjusted to 0.2 to 1 mm. In other words, the difference between the inner diameter of the outer tube (30) and the outer diameter including the fins (21) of the inner tube (20) is preferably adjusted to 0.4 to 2 mm. That is, when the gap (S) is too small, the inner tube (20) is restrained by the outer tube (30), so that the stress applied to the outer tube (30) greatly affects the inner tube (20). When the intermediate heat exchanger (10) composed of both the tubes (20) and (30) is bent, bending stress concentrates outside the bent portion of the fin (21) of the inner tube (20), and the fin (21 ) May cause problems such as cracks. On the other hand, when the gap (S) is too large, the size (length) of the fin (21) becomes small, and the heat transfer performance may be lowered and the heat exchange performance may be lowered.

  In the present embodiment, the number of fins (21) formed is preferably set to 13 to 18, more preferably 15 to 17. That is, when the number of fins is too small, the heat transfer performance may be reduced and the heat exchange performance may be reduced. On the other hand, when the number of fins is too large, the fin pitch is decreased, the width between the fins is decreased, the flow resistance of the refrigerant passing between the fins is increased, and the heat exchange performance may be deteriorated.

  Further, in the present embodiment, the thickness (T) of the fin (21) is set to 0.3 to 1.3 mm, more preferably 0.5 to 1.1 mm. That is, if the fin thickness (T) is too thin, it may be difficult to obtain sufficient strength. On the other hand, if the fin thickness (T) is too thick, the heat transfer performance and flow resistance are increased, which may reduce the heat exchange performance.

  Further, the circumferential opening angle (θ) between adjacent fins is preferably set to 15 to 30 °, more preferably 18 to 26 °. That is, when the opening angle (θ) is too small, the width between the fins is narrowed, the flow resistance of the refrigerant passing between them increases, and the heat exchange performance may be deteriorated. On the other hand, when the opening angle (θ) is too large, the number of fins becomes small, and there is a possibility that the heat transfer performance is lowered and the heat exchange performance is also lowered.

  As described above, according to the intermediate heat exchanger (10) of the present embodiment, since the finned inner tube (20) is inserted and arranged in the outer tube (30), both tubes (20) ( 30) can be formed separately and then both tubes (20) (30) can be combined. For this reason, for example, the fin (21), the tube wall, etc. can be formed thinly as compared with the case where the porous tube for heat exchanger is formed by a single extrusion, and a dense structure can be formed. The heat transfer performance and heat exchange performance can be reliably obtained.

  Furthermore, in this embodiment, since the clearance (S) is formed between the fin tip of the inner tube (20) and the inner peripheral surface of the outer tube (30), the inner tube (20) is connected to the outer tube ( 30), and when bending the intermediate heat exchanger (10), it is possible to prevent the bending stress from being concentrated outside the bent portion of the fin (21) of the inner tube (20). In addition, it is possible to reliably prevent problems such as cracks or breakage in the fin (21). Therefore, it can be easily and accurately bent into a desired shape, has excellent bending characteristics, and when applied to a refrigeration cycle for a car air conditioner, the desired shape can be adapted to the limited installation space in the automobile. It can be bent into a shape, and the degree of design freedom can be greatly improved.

  In addition, in the present embodiment, since the gap (S) is formed at the tip of the fin in the second heat exchange path (35), the refrigerant in the heat exchange path (35) mixes with the gap (S). Accordingly, it is possible to effectively prevent the temperature distribution of the refrigerant from being biased, and to further improve the heat exchange efficiency.

  In the above embodiment, the inner tube and the outer tube are made of aluminum or aluminum alloy. However, in the present invention, the materials of the inner tube and the outer tube are not particularly limited.

  Furthermore, in the said embodiment, although the case where this invention is applied to the refrigerating system for car air conditioners is mentioned as an example, the present invention is applicable also to other refrigerating systems other than a car air conditioner.

  Examples relating to the present invention will be described below.

<Example 1>
The intermediate heat exchanger (10) produced by inserting the inner tube (20) having the fins (21) formed on the outer periphery into the outer tube (30) as in the above embodiment is shown in the car shown in FIG. When applied to a refrigeration system for an air conditioner, the amount of heat exchange when changing the number of fins in the intermediate heat exchanger (10) (100% when the number of fins is “0”) is measured by computer simulation. did. The results are shown in Table 1 below.

  The conditions at this time were as follows: the length of the intermediate heat exchanger (length of the outer tube) was 500 mm, the outer diameter of the outer tube (30) was 21.0 mm, the inner diameter was 15.0 mm, and the inner tube (20) The outer diameter including the outer fin (21) is 14.0 mm, the outer diameter of the tube portion not including the outer fin (21) is 7.0 mm, and the inner diameter of the tube portion not including the inner fin (22) in the inner tube (20). Was 4.0 mm, and the inner diameter of the tube portion including the inner fin (22) was 3.5 mm.

<Example 2>
Under the same conditions as in Example 1 above, the passage resistance of the low-pressure refrigerant heat exchange path (the flow path between the inner tube and the outer tube) relative to the number of fins (when the number of fins is “0” is 100%) Measured by computer simulation. The results are shown in Table 2 below.

  As shown in Table 1, as the number of fins increases, the heat transfer improves and the amount of heat exchange increases. As shown in Table 2, as the number of fins increases, the passage resistance increases and the heat exchange performance increases. Decreases. When these are judged comprehensively, when the number of fins is 13 to 18, an appropriate amount of heat exchange can be obtained while suppressing the passage resistance to some extent, and particularly when the number of fins is 15 to 17, A sufficient amount of heat exchange can be obtained while sufficiently suppressing the passage resistance.

  Needless to say, when the number of fins is excessively small, the passage resistance is low, but it is difficult to obtain a sufficient amount of heat exchange, and the heat exchange performance is lowered as a whole. In addition, when the number of fins is excessively large, the heat exchange amount can be improved, but the passage resistance is increased and the heat exchange performance is lowered as a whole.

  The heat exchanger, intermediate heat exchanger, and refrigeration cycle of the present invention can be employed in a refrigeration system for car air conditioners, for example.

1 is a refrigerant circuit diagram of a refrigeration system for a car air conditioner to which an intermediate heat exchanger according to an embodiment of the present invention is applied. It is sectional drawing which shows the intermediate heat exchanger of embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 ... Intermediate heat exchanger 20 ... Inner tube 21 ... Fin 22 ... Inner fin 25 ... Heat exchange path for high-pressure refrigerant (first heat exchange path)
30 ... Outer tube 35 ... Low-pressure refrigerant heat exchange path (second heat exchange path)
S ... Gap

Claims (20)

  1. An inner tube provided with a plurality of fins on the outer periphery is inserted and arranged in the outer tube, and heat exchange is performed between the first fluid flowing through the inner tube and the second fluid flowing between the tubes. A heat exchanger,
    A heat exchanger, wherein a gap is formed between the inner peripheral surface of the outer tube and the tip of the fin.
  2.   2. The heat exchanger according to claim 1, wherein the plurality of fins are continuous along the length direction of the inner tube and are arranged at intervals in the circumferential direction.
  3.   The heat exchanger according to claim 1 or 2, wherein a gap between an inner peripheral surface of the outer tube and a tip of the fin is set to 0.2 to 1 mm.
  4.   The heat exchanger according to claim 1, wherein 13 to 18 fins are formed in a circumferential direction.
  5.   The heat exchanger according to any one of claims 1 to 4, wherein the fin has a thickness set to 0.3 to 1.3 mm.
  6.   The heat exchanger according to any one of claims 1 to 5, wherein an opening angle in a circumferential direction between adjacent fins is set to 15 to 30 °.
  7.   The heat exchanger according to claim 1, wherein the fin is formed integrally with the inner tube.
  8.   The heat exchanger according to any one of claims 1 to 7, wherein both the tubes are bent.
  9.   The heat exchanger according to any one of claims 1 to 8, wherein the first fluid is constituted by a high-pressure heat medium, and the second fluid is constituted by a low-pressure heat medium.
  10.   The heat exchanger according to any one of claims 1 to 9, wherein an inner fin is provided on an inner peripheral surface of the inner tube.
  11. Among the refrigerants circulating in the refrigeration cycle, an intermediate heat exchanger that exchanges heat between the high-pressure refrigerant and the low-pressure refrigerant,
    An inner tube provided with a plurality of fins on the outer periphery;
    In an aspect in which a gap is formed between an inner peripheral surface and the tip of the fin, an outer tube into which the inner tube is inserted and disposed,
    One of the high-pressure refrigerant and the low-pressure refrigerant is circulated through the first heat exchange path in the inner tube, and the other refrigerant is circulated through the second heat exchange path between the tubes. Intermediate heat exchanger.
  12.   The intermediate heat exchanger according to claim 11, wherein high-pressure refrigerant is circulated through the first heat exchange path and low-pressure refrigerant is circulated through the second heat exchange path.
  13.   The intermediate heat exchanger according to claim 11 or 12, wherein the refrigerant comprises carbon dioxide refrigerant.
  14. Among the refrigerants circulating in the refrigeration cycle, an intermediate heat exchanger that exchanges heat between a high-temperature refrigerant and a low-temperature refrigerant,
    An inner tube provided with a plurality of fins on the outer periphery;
    In an aspect in which a gap is formed between an inner peripheral surface and the fin, the outer tube is provided with the inner tube inserted and arranged,
    One of the high-temperature refrigerant and the low-temperature refrigerant is circulated through the first heat exchange path in the inner tube, and the other refrigerant is circulated through the second heat exchange path between the tubes. Intermediate heat exchanger.
  15. A refrigeration cycle in which the refrigerant circulates back through the compressor, condenser, decompressor and evaporator back to the compressor,
    An intermediate heat exchanger for exchanging heat between the high-pressure refrigerant flowing through the high-pressure circuit from the compressor to the decompressor and the low-pressure refrigerant flowing through the low-pressure circuit from the decompressor to the compressor;
    The intermediate heat exchanger is
    An inner tube provided with a plurality of fins on the outer periphery;
    In an aspect in which a gap is formed between an inner peripheral surface and the tip of the fin, an outer tube into which the inner tube is inserted and arranged,
    One of the high-pressure refrigerant and the low-pressure refrigerant is circulated through the first heat exchange path in the inner tube, and the other refrigerant is circulated through the second heat exchange path between the tubes. Refrigeration cycle to be.
  16. A refrigeration cycle in which the refrigerant circulates back through the compressor, condenser, decompressor and evaporator back to the compressor,
    An intermediate heat exchanger for exchanging heat between the high-pressure refrigerant flowing between the condenser and the decompressor and the low-pressure refrigerant flowing between the evaporator and the compressor;
    The intermediate heat exchanger is
    An inner tube provided with a plurality of fins on the outer periphery;
    In an aspect in which a gap is formed between an inner peripheral surface and the tip of the fin, an outer tube into which the inner tube is inserted and arranged,
    One of the high-pressure refrigerant and the low-pressure refrigerant is circulated through the first heat exchange path in the inner tube, and the other refrigerant is circulated through the second heat exchange path between the tubes. Refrigeration cycle to be.
  17.   The refrigeration cycle according to claim 16, wherein high-pressure refrigerant is circulated through the first heat exchange path and low-pressure refrigerant is circulated through the second heat exchange path.
  18.   The refrigeration cycle according to claim 16 or 17, wherein the condenser comprises a gas cooler.
  19.   The refrigeration cycle according to any one of claims 16 to 18, wherein the refrigerant comprises a carbon dioxide refrigerant.
  20.   The refrigeration cycle according to any one of claims 16 to 19, wherein both tubes as the intermediate heat exchanger are bent.
JP2005224926A 2004-08-06 2005-08-03 Heat exchanger, intermediate heat exchanger, and refrigeration cycle Pending JP2006071270A (en)

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JP2004230778 2004-08-06
JP2005224926A JP2006071270A (en) 2004-08-06 2005-08-03 Heat exchanger, intermediate heat exchanger, and refrigeration cycle

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JP2005224926A JP2006071270A (en) 2004-08-06 2005-08-03 Heat exchanger, intermediate heat exchanger, and refrigeration cycle

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US (1) US20080066488A1 (en)
JP (1) JP2006071270A (en)
CN (1) CN1977139A (en)
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WO (1) WO2006014032A1 (en)

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JP2009204166A (en) * 2008-02-26 2009-09-10 Showa Denko Kk Double pipe heat exchanger
JP2009204271A (en) * 2008-02-29 2009-09-10 Tgk Co Ltd Refrigerating cycle
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DE112005001885T5 (en) 2007-06-21

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