JP2015092122A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain a small heat exchanger which achieves excellent reliability by providing a heat insulation part that inhibits freezing of a fluid.SOLUTION: A heat exchanger includes: a first refrigerant passage 1 where a first fluid flows along a first axis X direction; a second refrigerant passage 2 where a second fluid, which conducts heat exchange with the first fluid, flows along the first refrigeration passage 1; a first inlet header 3 and a first outlet header 4 which are connected with both ends of the first refrigerant passage 1; a second inlet header 5 and a second outlet header 6 which are connected with both ends of the second refrigerant passage 2; and a heat insulation part 21 which inhibits heat exchange between the first fluid and the second fluid and is located between the first refrigerant passage 1 and the second refrigerant passage 2 at end parts of the first refrigerant passage 1 and the second refrigerant passage 2.

Description

  The present invention relates to a heat exchanger that performs heat exchange between fluids.

  As a conventional heat exchanger, a flat first refrigerant channel through which a low-temperature fluid flows, a flat second refrigerant channel through which a high-temperature fluid flows in parallel with the low-temperature fluid, and both ends of the first refrigerant channel are connected. The first header and the second header connected to both ends of the second refrigerant flow path are provided, and the flat surfaces of the first refrigerant flow path and the second refrigerant flow path are contact-laminated by brazing or the like A heat exchanger is known (see, for example, Patent Document 1).

JP 2002-340485 A (page 8, FIG. 1)

However, in the conventional heat exchanger, the fluid may be locally cooled excessively due to the disturbance of the fluid flow, and the fluid may freeze in the flow path. For this reason, in the conventional heat exchanger, there existed a problem that the flow volume of the fluid which flows through a flow path will fall. Furthermore, in the conventional heat exchanger, there is a possibility that the flow path may be blocked due to the progress of freezing, and the flow path may be damaged due to volume expansion of the frozen fluid.
In order to suppress the occurrence of freezing, the temperature of the low-temperature fluid that exchanges heat with the high-temperature fluid may be increased. In this case, the heat exchanger is increased in size to obtain a desired heat exchange amount. There was a problem.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to obtain a small heat exchanger having excellent reliability by providing a heat insulating portion that suppresses freezing of fluid.

  In the heat exchanger according to the present invention, the first refrigerant flow path along which the first fluid flows along the first axial direction, and the second fluid that exchanges heat with the first fluid flow along the first refrigerant flow path. Second refrigerant flow path, first inlet header and first outlet header connected to both ends of the first refrigerant flow path, second inlet header connected to both ends of the second refrigerant flow path and second 2 at the end of the outlet header, the first refrigerant flow path, and the second refrigerant flow path, and disposed between the flow paths to suppress heat exchange between the first fluid and the second fluid. And a heat insulating part.

  According to the heat exchanger according to the present invention, since the heat insulating portion that suppresses heat exchange between the fluids is disposed in the vicinity where the fluid flow is disturbed, the fluid is locally cooled excessively, Freezing of the fluid can be suppressed. As a result, according to the present invention, a small heat exchanger having excellent reliability can be obtained.

It is the perspective view and sectional drawing of the heat exchanger which concern on Embodiment 1 of this invention. It is the elements on larger scale of the heat exchanger shown in FIG. 1, and its comparative example. It is the perspective view and sectional drawing of the heat exchanger which concern on Embodiment 2 of this invention. It is sectional drawing which shows the other example of the heat insulation part of the heat exchanger shown in FIG. It is a graph which shows the relationship between the distance from the position where the disorder | damage | failure of the flow of the fluid generate | occur | produced, the internal diameter of a flow path, and the increase rate of a heat transfer characteristic.

Embodiment 1 FIG.
Fig.1 (a) is an external appearance perspective view of the heat exchanger 8 which concerns on Embodiment 1 of this invention, FIG.1 (b) is AA sectional drawing of Fig.1 (a). In the following description, the same reference numerals in the drawings are the same or equivalent, and this is common throughout the entire specification.

  The heat exchanger 8 according to Embodiment 1 is a type of heat exchanger that uses a gas-liquid two-phase refrigerant such as a fluorocarbon, hydrocarbon, or carbon dioxide as a low-temperature refrigerant, and uses water as a high-temperature refrigerant. For example, it is incorporated into a refrigeration cycle apparatus. As shown in FIGS. 1 (a) and 1 (b), the heat exchanger 8 includes a first refrigerant channel 1, a second refrigerant channel 2, a first inlet header 3, a first outlet header 4, and a second refrigerant channel. It has an inlet header 5 and a second outlet header 6.

  The first refrigerant channel 1 is a channel through which a low-temperature refrigerant flows along the X-axis direction that is the first axis. The first refrigerant flow path 1 has a flat cross section, and is configured by arranging a plurality of first heat transfer paths 1a in parallel along the Y axis direction intersecting the X axis. In the following description, the X axis, the Y axis, and the Z axis are described as being orthogonal to each other, but the X axis, the Y axis, and the Z axis may intersect at an angle other than a right angle. . Each first heat transfer path 1a is a through hole having a flat cross section, and a flow path through which a low-temperature refrigerant flows is formed therein. A first inlet header 3 and a first outlet header 4 extending along the Y-axis direction are connected to both ends of the first refrigerant flow path 1.

  The second refrigerant flow path 2 is disposed along the parallel direction of the first refrigerant flow path 1 and is a flow path through which the high-temperature refrigerant flows. The high temperature refrigerant flowing through the second refrigerant flow path 2 flows in parallel with the low temperature refrigerant flowing through the first refrigerant flow path 1. The second refrigerant channel 2 has a straight portion 2L extending along the X-axis direction and a bent portion 2R formed on both sides of the straight portion 2L. The second refrigerant flow path 2 has a flat cross section, and is configured by arranging a plurality of second heat transfer paths 2a in parallel along the Y-axis direction. Each second heat transfer path 2a is a through hole having a flat cross section, and a flow path through which a high-temperature refrigerant flows is formed inside. A second inlet header 5 and a second outlet header 6 extending along the direction intersecting the second refrigerant flow path 2 are connected to both ends of the second refrigerant flow path 2. In this embodiment, as described above, the configuration may be such that the low-temperature refrigerant flows through the first refrigerant flow path 1 and the high-temperature refrigerant flows through the second refrigerant flow path 2, or the first refrigerant flow The configuration may be such that the high-temperature refrigerant flows in the path 1 and the low-temperature refrigerant flows in the second refrigerant flow path 2.

  The first refrigerant channel 1 and the second refrigerant channel 2 are made of a material having good thermal conductivity such as aluminum, aluminum alloy, copper, copper alloy, steel, and stainless alloy steel. For example, the first refrigerant channel 1 and the second refrigerant channel 2 can be formed by extrusion molding or pultrusion molding. Further, for example, the first refrigerant channel 1 and the second refrigerant channel 2 can be formed by bending a flat plate by roll forming or the like and then electro-sewing (welding) seams at both ends of the flat plate. Further, for example, the first refrigerant channel 1 and the second refrigerant channel 2 are formed by roll molding or press molding a cylindrical material.

  The first refrigerant flow path 1 and the second refrigerant flow path 2 are joined by brazing flat surfaces facing each other. For example, the flat surface of the first refrigerant channel 1 and the flat surface of the second refrigerant channel 2 are joined by a brazing material such as an aluminum-silicon system. At the junction 20 between the first refrigerant flow path 1 and the second refrigerant flow path 2, the low temperature refrigerant flowing through the first refrigerant flow path 1 and the high temperature refrigerant flowing through the second refrigerant flow path 2 can perform heat exchange. . A gap is formed between the first refrigerant channel 1 and the second refrigerant channel 2 on both sides of the joint 20 along the direction in which the low-temperature refrigerant and the high-temperature refrigerant flow. The heat insulation part 21 which suppresses heat exchange with the flow path 1 and the 2nd refrigerant flow path 2 is comprised.

Next, the operation of the heat exchanger according to this embodiment will be described.
For example, the low-temperature refrigerant in the gas-liquid two-phase state is supplied to the first refrigerant flow path 1 through the first inlet header 3. The low-temperature refrigerant that has exchanged heat with the high-temperature refrigerant in the first refrigerant flow path 1 flows out to the first outlet header 4.
Further, the high-temperature refrigerant such as water is supplied to the second refrigerant flow path 2 through the second inlet header 5. The high-temperature refrigerant cooled in the second refrigerant flow path 2 flows out to the second outlet header 6.
In the above description, the low-temperature refrigerant flowing through the first refrigerant flow path 1 and the high-temperature refrigerant flowing through the second refrigerant flow path 2 have been described with respect to the parallel flow type heat exchanger. It may be a counterflow type heat exchanger in which the flow direction and the flow direction of the high-temperature refrigerant face each other.

Fig.2 (a) is the elements on larger scale of the heat exchanger shown in FIG. 1, FIG.2 (b) is a comparative example (prior art) of Fig.2 (a). In the comparative example, as shown in FIG. 2B, freezing has occurred on the inner wall surface of the second refrigerant flow path 2 (freezing portion 2F). In the comparative example, this is caused by excessively cooling the high-temperature refrigerant in a place where the flow of the low-temperature refrigerant and the high-temperature refrigerant is disturbed and locally having high cooling performance.
The disturbance of the flow of the low-temperature refrigerant flowing through the first refrigerant flow path 1 occurs due to a change in the direction and speed of the flow of the low-temperature refrigerant at the communication portion between the first inlet header 3 and the first refrigerant flow path 1. .
The turbulence of the flow of the high-temperature refrigerant flowing through the second refrigerant flow path 2 is caused by the flow of the high-temperature refrigerant at the communication portion between the second inlet header 5 and the second refrigerant flow path 2 and the bent portion 2R of the second refrigerant flow path. This is caused by a change in the direction and speed of the.
As described above, in the comparative example, since the cooling performance is locally increased in a place where the flow of the low-temperature refrigerant and the high-temperature refrigerant is disturbed, the high-temperature refrigerant is excessively cooled locally, and the frozen portion 2F is generated. Since the freezing part 2F becomes the flow path resistance of the second refrigerant flow path 2, in the comparative example, the flow rate of the high-temperature refrigerant is decreased, and the heat exchange characteristics of the heat exchanger are significantly decreased. Furthermore, when the freezing progresses, there is a possibility that the flow path of the second refrigerant flow path 2 may be blocked, and that the second refrigerant flow path 2 may be damaged due to the volume expansion of the frozen high-temperature refrigerant.

  Compared with the comparative example shown in FIG. 2B, the heat exchanger 8 according to Embodiment 1 shown in FIG. 2A is provided between the first refrigerant flow path 1 and the second refrigerant flow path 2. A heat insulating portion 21 is formed. The heat insulating portion 21 is formed so as to extend to the joint portion 20 side with respect to the first inlet header 3, the second inlet header 5, and the bent portion 2 R, and the first refrigerant channel 1 and the second refrigerant channel 2 Suppresses heat exchange. As a result, in the heat exchanger 8 according to the first embodiment, heat exchange is suppressed by the heat insulating portion 21 in a region where the flow of the low-temperature refrigerant and the high-temperature refrigerant is disturbed. And in the heat exchanger of this embodiment, the junction part 20 which performs heat exchange with the 1st refrigerant | coolant flow path 1 and the 2nd refrigerant | coolant flow path 2 in the area | region where the disturbance of the flow of the low-temperature refrigerant | coolant and the high-temperature refrigerant | coolant was reduced. Is formed. For this reason, in the heat exchanger 8 according to the first embodiment, the problem of freezing of the high-temperature fluid in the second refrigerant flow path 2 due to excessively local cooling of the high-temperature fluid due to fluid flow disturbance is solved. Has been. Therefore, in Embodiment 1, a small heat exchanger with excellent reliability is provided.

  In addition, as shown in FIG.1 (b), the heat insulation part 21 may be formed in the both sides of the junction part 20 along the direction through which a low temperature refrigerant | coolant and a high temperature refrigerant | coolant flow. In this case, it is possible to prevent the freezing of the high temperature fluid even when the flow directions of the low temperature refrigerant and the high temperature refrigerant are not determined in advance or when the flow directions of the low temperature refrigerant and the high temperature refrigerant are switched during operation. it can.

Embodiment 2. FIG.
Fig.3 (a) is an external appearance perspective view of the heat exchanger 8 which concerns on Embodiment 2 of this invention, FIG.3 (b) is BB sectional drawing of Fig.3 (a). The heat exchanger 8 according to Embodiment 2 is a type of heat exchanger that uses a gas-liquid two-phase refrigerant such as a fluorocarbon, hydrocarbon, or carbon dioxide as a low-temperature refrigerant, and uses water as a high-temperature refrigerant. For example, it is incorporated into a refrigeration cycle apparatus.

  As shown in FIGS. 3A and 3B, the heat exchanger 8 includes a first refrigerant path 101 corresponding to the first refrigerant flow path, a second refrigerant path 102 corresponding to the second refrigerant flow path, A refrigerant flow path including a first inlet communication hole 103a corresponding to the first inlet header, a first outlet communication hole 104a corresponding to the first outlet header, a second inlet header 105, and a second outlet header 106; The refrigerant flow path is arranged in the block body 100.

  The block 100 and the refrigerant flow path formed in the block 100 can be manufactured by extrusion and pultrusion of aluminum and aluminum alloy, copper and copper alloy, and steel and stainless alloy steel. Note that the first refrigerant path 101 and the block body 100 may be configured integrally, or the first refrigerant path 101 and the block body 100 are configured separately, and the first refrigerant path 101 and the block body 100 are separated from each other. It may be configured to be joined by attaching or the like.

  The first refrigerant path 101 is a flow path through which a low-temperature refrigerant flows along the X-axis direction. The first refrigerant path 101 has a flat cross section, and is configured by arranging a plurality of first heat transfer paths 101a in parallel along the Y-axis direction. Each first heat transfer path 101a is a rectangular through hole formed in the block body 100, and has a flow path through which a low-temperature refrigerant flows. A first inlet communication hole 103 a and a first outlet communication hole 104 a that extend along the Y-axis direction and communicate with the first refrigerant path 101 are connected to both sides of the first refrigerant path 101. Note that both ends of the first refrigerant path 101 are sealed by a sealing process such as a pinch process or a sealing member.

  As shown in FIG. 3B, turbulence is suppressed near the connection portion between the first refrigerant path 101 and the first inlet communication hole 103a and near the connection portion between the first refrigerant path 101 and the first outlet communication hole 104a. A portion 111 is formed. The turbulence suppression unit 111 is configured to adjust the cross-sectional area of the flow path, and is between the first refrigerant path 101 and the first inlet communication hole 103a or between the first refrigerant path 101 and the first outlet communication hole 104a. About the flowing low-temperature refrigerant, the fluid velocity is adjusted so as not to suddenly accelerate or decelerate, thereby suppressing disturbance of the fluid flow. The turbulence suppressing unit can be applied to all portions where the direction and speed of the fluid change. For example, the turbulence suppressing unit suppresses the occurrence of the flow turbulence by chamfering or rounding the corners.

  One end of the first inlet communication hole 103a and the first outlet communication hole 104a is connected to the first inlet connection pipe 103 or the first outlet connection pipe 104 that communicates with the outside. The other end of the outlet communication hole 104a is a sealing hole or sealed with a sealing member.

  The 2nd refrigerant | coolant path | pass 102 is arrange | positioned along the parallel direction of the 1st refrigerant | coolant path | pass 101, and is a flow path through which a high temperature refrigerant | coolant flows. The high-temperature refrigerant that flows through the second refrigerant path 102 flows in parallel with the low-temperature refrigerant that flows through the first refrigerant path 101. The second refrigerant path 102 has a flat cross section and is configured by arranging a plurality of second heat transfer tubes 102a in parallel along the Y-axis direction. Each second heat transfer tube 102a has a circular cross section, and a flow path through which the high-temperature refrigerant flows is formed inside.

  In this embodiment, a through hole 110 is formed in the block body 100, and each second heat transfer tube 102 a is inserted into the through hole 110. Each of the second heat transfer tubes 102 a is in close contact with at least a part of the through hole 110, and this part forms a bonding region 120. The low temperature refrigerant flowing through the first refrigerant path 101 and the high temperature refrigerant flowing through the second refrigerant path 102 can exchange heat in the joining region 120. The second heat transfer tube 102a is made of, for example, copper or stainless steel, and is corrosive to water. By configuring the second heat transfer tube 102a with copper or stainless steel and the other components with aluminum or aluminum alloy, it is possible to obtain an inexpensive and metered heat exchanger while ensuring the corrosion resistance of the second refrigerant path 102. Can do. A second inlet header 105 and a second outlet header 106 extending along a direction intersecting the second refrigerant path 102 are connected to both ends of the second refrigerant path 102.

  As shown in FIG.3 (b), the through-hole 110 of the block body 100 is the 1st internal peripheral surface 110a closely_contact | adhered to each 2nd heat exchanger tube 102a, and the 1st internal peripheral surface on both sides of the 1st internal peripheral surface 110a. And a second inner peripheral surface 110b having a larger diameter than 110a. A gap is formed between the second inner peripheral surface 110b and each of the second heat transfer tubes 102a, and the gap is a heat insulating portion 121 that suppresses heat exchange between the first refrigerant channel 1 and the second refrigerant channel 2. Configure. For example, the second inner peripheral surface 110b can be formed relatively easily by a subsequent process such as counterboring.

なお、上記の数式１において、ｌは拡管後の第２伝熱管１０２ａの直径［ｍｍ］、ｍは第１内周面１１０ａの直径［ｍｍ］とする。 Each second heat transfer tube 102a is inserted into the through hole 110 of the block body 100, and then expanded and adhered to the first inner peripheral surface 110a. For example, an example in which the diameter of the second heat transfer tube 102a is 8 mm will be described below.
When the tube expansion rate of the second heat transfer tube 102a is 3% to 7%, the contact thermal resistance becomes low when the adhesion rate δ [%] expressed by the following formula 1 is 1 to 3%, which is preferable. .

In the above mathematical formula 1, l is the diameter [mm] of the second heat transfer tube 102a after the expansion, and m is the diameter [mm] of the first inner peripheral surface 110a.

  In the above case, the diameter of the second heat transfer tube 102a after the expansion is about 8.24 to 8.56 mm. At this time, the inner diameter of the second inner peripheral surface 110b is set so that a gap as a heat insulating portion is formed between the second inner peripheral surface 110b and each second heat transfer tube 102a. That is, the inner diameter of the second inner peripheral surface 110b is set larger than the diameter of the second heat transfer tube 102a after the pipe expansion. Here, the width of the gap is preferably about 1 mm from the request for downsizing of the heat exchanger. Therefore, in the example where the diameter of the second heat transfer tube 102a is 8 mm, the inner diameter of the second inner peripheral surface 110b is 10.42 to 10.56 mm.

Next, the operation of the heat exchanger according to this embodiment will be described.
For example, the low-temperature refrigerant in the gas-liquid two-phase state is supplied to the first refrigerant path 101 through the first inlet communication hole 103a. The low-temperature refrigerant that has exchanged heat with the high-temperature refrigerant in the first refrigerant path 101 flows out to the first outlet communication hole 104a.
Further, the high-temperature refrigerant such as water is supplied to the second refrigerant path 102 through the second inlet header 105. The high-temperature refrigerant cooled in the second refrigerant path 102 flows out to the second outlet header 106.
In the above description, the parallel flow type heat exchanger in which the low temperature refrigerant flowing in the first refrigerant path 101 and the high temperature refrigerant flowing in the second refrigerant path 102 flow in the same direction has been described. And a counter-flow heat exchanger in which the flow direction of the high-temperature refrigerant is opposed to each other.

  The heat exchanger 8 according to this embodiment includes a heat insulating part 121 between the first refrigerant path 101 and the second refrigerant path 102. The heat insulation part 121 on the first inlet communication hole 103a and the second inlet header 105 side is formed so as to extend to the joining region 120 side than the first inlet communication hole 103a, the second inlet header 105 and the turbulence suppressing part 111. Yes, heat exchange between the first refrigerant path 101 and the second refrigerant path 102 is suppressed. For this reason, in the heat exchanger 8 according to this embodiment, in the region where the flow of the low-temperature refrigerant and the high-temperature refrigerant is disturbed, the heat exchange is suppressed by the heat insulating portion 121, and the low-temperature refrigerant and the high-temperature refrigerant A joining region 120 that performs heat exchange between the first refrigerant path 101 and the second refrigerant path 102 is disposed in a region where the turbulence of the flow is reduced. Furthermore, in the heat exchanger 8 according to Embodiment 2, the turbulence suppression unit 111 is formed in the vicinity of the connection portion between the first heat transfer path 101a and the first inlet communication hole 103a, and flow turbulence occurs. Is suppressed. As a result, in the heat exchanger 8 according to this embodiment, the problem that the fluid is locally excessively cooled due to the disturbance of the fluid flow and the fluid freezes in the flow path is solved. In addition, as shown in FIG.3 (b), the heat insulation part 121 may be formed in the both sides of the joining area | region 120 along the direction through which a low temperature refrigerant | coolant and a high temperature refrigerant | coolant flow.

なお、数式２において、ｄは第２冷媒パス１０２の内径［ｍｍ］、ｘは流体の流れの乱れが発生した位置からの距離［ｍｍ］である。上記の例では、流路の断面形状が円形であったので、ｄは内径であったが、断面がその他の形状の場合には、ｄを水力直径または相当径に置き換えることによって、上記の式に適用することができる。 Next, an example of the relationship between the distance from the position where the fluid flow turbulence has occurred, the diameter of the flow path, and the rate of increase in heat transfer characteristics will be described with reference to the example shown in FIG. For example, in the example of FIG. 3B, the high-temperature refrigerant that has flowed into the second refrigerant path 102 from the second inlet header 105 is in the communication portion between the second inlet header 105 and the second refrigerant path 102, and its direction and speed. The flow is disturbed due to the change of. This turbulent flow of the high-temperature refrigerant is a flow developed by the high-temperature refrigerant being attenuated and progressing along the second refrigerant path 102 toward the second outlet header 106. At this time, the undeveloped flow in which the turbulence is generated has a thin boundary layer on the wall surface side and an increased heat transfer characteristic as compared with the developed flow in which the turbulence is attenuated. The change in the increase rate ε of the heat transfer characteristic is expressed by the following formula 2 in the case of a single phase flow such as water.

In Equation 2, d is the inner diameter [mm] of the second refrigerant path 102, and x is the distance [mm] from the position where the fluid flow disturbance occurs. In the above example, since the cross-sectional shape of the flow path was circular, d was an inner diameter. However, when the cross-section has another shape, the above equation is obtained by replacing d with a hydraulic diameter or an equivalent diameter. Can be applied to.

  FIG. 5 is a graph showing x / d on the horizontal axis and ε on the vertical axis. As shown in FIG. 5, as the distance x from the position where the fluid flow turbulence is increased, the rate of increase ε of the heat transfer characteristics is rapidly attenuated and stabilized. Specifically, when x / d is 1 or more, the increase rate ε decreases, and the change rate also decreases, which is stable. Therefore, in the example shown in FIG. 3B, for example, the length of the heat insulating portion 121 (the counterbore processing portion) is set so that the distance x from the first inlet communication hole 103a is equal to the inner diameter d of the second refrigerant path 102. To decide. More preferably, the distance x is 2d or more, and further preferably, the distance x is 3d or more. However, by configuring the distance x to be long, there is a problem that the influence of the decrease in heat transfer characteristics is increased, and the heat exchanger is increased in size. Therefore, the length of the distance x of the heat insulating portion is appropriately determined using the above-described Equation 2 and FIG.

  In the above description, as shown in FIG. 3B, the heat insulating portion 121 is configured by forming a gap between the second inner peripheral surface 110b and the outer peripheral surface of the second heat transfer tube 102a. As shown in FIG. 4, the heat insulating portion 121 a may be configured by forming a slit between the first refrigerant path 101 and the second refrigerant path 102. Moreover, the structure provided with both a slit and a clearance gap may be sufficient.

  The present invention is not limited to the above-described embodiment, and various modifications can be made within the scope of the present invention. That is, the configuration of the above embodiment may be improved as appropriate, or at least a part of the configuration may be replaced with another configuration. Further, the configuration requirements that are not particularly limited with respect to the arrangement are not limited to the arrangement disclosed in the embodiment, and can be arranged at a position where the function can be achieved.

  For example, in the above embodiment, the heat insulating portion is configured by a space such as a gap, but a heat insulating material such as a resin having a lower thermal conductivity than the surrounding atmosphere may be disposed in the space.

  Further, the cross-sectional shape of the flow path is not limited to a rectangle or a circle, and can be appropriately changed according to desired heat exchange efficiency and pressure resistance performance. Further, the flow path through which the high-temperature fluid flows and the flow path through which the low-temperature fluid flows may have the same shape and quantity, or may have different shapes and quantities. These can be set as appropriate in accordance with the operating conditions of the heat exchanger, the heat of the refrigerant, and the fluid property values.

  Further, a groove may be formed on the inner surface of the flow path in order to promote heat transfer. For example, manufacturing simplification can be achieved by simultaneously processing the grooves during extrusion and pultrusion.

  DESCRIPTION OF SYMBOLS 1 1st refrigerant | coolant flow path, 1a 1st heat transfer path, 2nd 2nd refrigerant flow path, 2F freezing part, 2L straight line part, 2R bending part, 2a 2nd heat transfer path, 3rd 1st inlet header, 4th 1st exit Header, 5 second inlet header, 6 second outlet header, 8 heat exchanger, 20 joint portion, 21 heat insulating portion, 100 block body, 101 first refrigerant path, 101a first heat transfer path, 102 second refrigerant path, 102a second heat transfer pipe, 103 first inlet connection pipe, 103a first inlet communication hole, 104 first outlet connection pipe, 104a first outlet communication hole, 105 second inlet header, 106 second outlet header, 110 through hole, 110a 1st inner peripheral surface, 110b 2nd inner peripheral surface, 111 disorder | damage | failure suppression part, 120 joining area | region, 121 heat insulation part, 121a heat insulation part.

Claims (11)

A first refrigerant flow path in which the first fluid flows along the first axial direction;
A second refrigerant flow path in which the second fluid that exchanges heat with the first fluid flows along the first refrigerant flow path;
A first inlet header and a first outlet header connected to both ends of the first refrigerant flow path;
A second inlet header and a second outlet header connected to both ends of the second refrigerant flow path;
A heat insulating portion disposed between the first refrigerant flow path and the second refrigerant flow path to suppress heat exchange between the first fluid and the second fluid; A heat exchanger, comprising: The first refrigerant flow path is composed of a plurality of through holes arranged in parallel along a second axial direction intersecting the first axial direction,
2. The heat exchanger according to claim 1, wherein the second refrigerant flow path includes a plurality of through holes arranged in parallel in a layer parallel to the first refrigerant flow path.   The heat exchanger according to claim 1 or 2, wherein the first refrigerant channel and the second refrigerant channel have a flat shape.   The heat insulating portion is disposed on the first inlet header and the second inlet header side, and extends from the first inlet header and the second inlet header to the first outlet header and the second outlet header side. A first heat insulating portion, disposed on the first outlet header and the second outlet header side, and closer to the first inlet header and the second inlet header side than the first outlet header and the second outlet header. The heat exchanger according to any one of claims 1 to 3, further comprising a second heat insulating portion formed to extend. The second refrigerant flow path includes a straight portion extending along the first axial direction, and bent portions formed on both sides of the straight portion,
5. The heat exchanger according to claim 1, wherein the heat insulating portion is formed to extend toward the straight portion from the bent portion.   The said heat insulation part is a gap | interval formed in the both sides of the junction part which joined the said 1st refrigerant flow path and the said 2nd refrigerant flow path, The any one of Claims 1-5 characterized by the above-mentioned. The heat exchanger as described in.   The heat exchanger according to any one of claims 1 to 6, wherein the first refrigerant channel and the second refrigerant channel are integrally formed. The second refrigerant flow path is configured by a tube that is inserted into a block body through hole formed in the block body and is in close contact with the block body through hole,
The heat exchanger according to any one of claims 1 to 7, wherein the pipe is made of a material having corrosion resistance to water.   The heat exchanger according to claim 8, wherein the first refrigerant flow path is formed in the block body. The block body through-hole has a second inner peripheral surface formed with a larger diameter than the first inner peripheral surface that contacts the second refrigerant flow path,
The heat exchanger according to claim 8 or 9, wherein the heat insulating portion is a gap formed between the second refrigerant flow path and the second inner peripheral surface.   The said heat insulation part is a slit formed in the said block body between the said 1st refrigerant flow path and the said 2nd refrigerant flow path, The any one of Claims 8-10 characterized by the above-mentioned. The described heat exchanger.

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