JP2005127529A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger for maximizing its performance by making effective use of the whole heat exchanger even when utilizing the parallel flow type heat exchanger using a flat tube as an evaporator or a condenser. <P>SOLUTION: The heat exchanger comprises the flat tube 1 vertically inserted at both ends into right and left headers 3, 4 so that refrigerant smoothly passes through the flat tube 1. A fin 2 is provided for promoting heat exchange between the refrigerant and air and connection pipes 5, 6 to be guided to a refrigerating cycle are installed in the hollow cylindrical right and left headers 3, 4, thus allowing the effective use of the whole heat exchanger in a well balanced manner. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a heat exchanger used in a heat pump air conditioner, and more particularly to a heat exchanger that effectively uses the entire heat exchanger and can efficiently exchange heat between refrigerant and air.

  Conventionally, fin-and-tube type heat exchangers constituting this type of air conditioner refrigeration cycle system have a small amount of refrigerant circulation and low pressure loss in the heat transfer tubes when the heat exchange capacity is small. Because it is small, a single refrigerant passage is sufficient, but when the amount of heat exchange is large, a large amount of refrigerant is circulated, and the pressure loss in the heat transfer tube increases, so that the parallel flow type is configured with multiple refrigerant passages And serpentine type heat exchangers are required.

  Here, in FIG. 12, a case where a parallel flow type heat exchanger having high heat exchange efficiency is used for the evaporator will be described. In the case of the conventional example shown in FIG. 12, 3 and 4 are hollow cylindrical left and right headers, one of which is closed, but inside, partition plates 7 and 8 are respectively installed, whereby left and right headers 3 4 The interior is divided into two chambers. For example, when this heat exchanger is used as an evaporator, a gas / liquid two-phase gas refrigerant flows from the refrigeration cycle through the connecting pipe 6 joined to the lower side of the right header 4, and a partition plate inside the right header 4. 8, once passing through the pipe group C communicating from the right header 4 to the left header 3, and further, by the partition plate 7, each of the pipe groups B and C meanders into an S shape and flows. Heat exchange with air is performed through the fins 2 that are in close contact with the flat tube 1, and the gasified refrigerant finally flows out from the connection tube 5 at the upper part of the left header 3 that has a hollow cylindrical shape to the refrigeration cycle. The series of refrigerant flows inside the evaporator is indicated by broken line arrows in the schematic diagram of FIG.

  Further, when this heat exchanger is used as a condenser, the direction of refrigerant flow is reversed from that of the evaporator due to switching of the four-way valve in the refrigeration cycle. In the case of the conventional example shown in FIG. ) The high-temperature and high-pressure single-phase superheated refrigerant gas discharged from the refrigerant flows into the connection pipe 5 at the upper part of the left header 3 from the connection pipe 5 and is temporarily blocked by the partition plate 7 of the left header 3. Each of the flat tubes passes through the pipe line group A communicating with the right header 4 and meanders the pipe group groups B and C in an S-shape as shown in the schematic diagram of the refrigerant flow indicated by the solid arrows in FIG. Heat exchange with air is performed through fins 2 that are in close contact with 1, and the condensed and liquefied refrigerant flows out from the connection pipe 5 of the right header 4 that has a hollow cylindrical shape to the refrigeration cycle.

  Usually, 1 is a flat tube 1 for a heat exchanger having a flat cross-sectional outer shape made of a metal such as aluminum or copper alloy having good thermal conductivity, and has one or several refrigerant passages inside, and a lower header 4 A plurality of the headers 3 are vertically attached to bridge the headers so as to communicate with the upper header 3.

Conventionally, as a configuration example in which the heat exchange efficiency of such a heat exchanger for an air conditioner is improved, it is divided into two or more passage groups so that the entire heat exchanger can be operated efficiently. (For example, refer to Patent Document 1) and serpentine type heat exchangers that are configured with a limited number of tubes (for example, refer to Patent Document 2).
JP 63-161393 (page 4, Fig. 1) JP-A-2-13788 (page 4, Fig. 2)

However, in the conventional configuration, when a heat exchanger composed of a parallel flow type or serpentine type flat tube is used in this way, the condenser has a refrigerant state gasified at a high temperature from the inlet side. In general, the refrigerant is generally configured so that the number of tubes gradually decreases so that the refrigerant is liquefied while dissipating heat and is directed to the outlet side of the condenser which becomes supercooled liquid, and further the heat transfer area is reduced. The performance of the heat exchanger varies greatly depending on the configuration of the number of tubes. For example, if the number of tubes is extremely reduced toward the outlet of the condenser, or if the cross-sectional area of the tubes is reduced, the refrigeration cycle performance will decrease due to an increase in the pressure loss of the refrigerant. In this case, the deterioration of performance becomes more remarkable. In addition, when the number of tubes is gradually reduced or the cross-sectional area is reduced, the heat exchanger performance deteriorates as the flow rate of the supercooled liquid at the outlet of the condenser with a reduced heat transfer rate decreases. Since a large liquid refrigerant stays, there is a problem that a problem such as an increase in the amount of refrigerant in the entire refrigeration cycle system occurs.

  The present invention solves such a conventional problem, and even when a heat exchanger composed of a flat tube is used as an evaporator or a condenser, the entire heat exchanger is effectively used, and the heat exchanger It is an object of the present invention to provide a heat exchanger that can obtain a sufficient amount of heat exchange by designing an optimal number of flat tubes that can bring out the maximum performance.

  In order to solve the conventional problems, a heat exchanger according to the present invention includes a pair of headers extending at a predetermined distance, and a plurality of refrigerant circulation holes through which refrigerant flows between the pair of headers. A heat exchanger having a flat tube formed with the fins disposed between the adjacent flat tubes, and the header has a structure capable of partitioning the flow of the refrigerant. When the heat exchanger is used as an evaporator, the number of the flat tubes from which the refrigerant finally flows out is in a range of 1 to 2.5 times the number of the flat tubes from which the refrigerant first flows. It constitutes.

  Further, a pair of headers extending at a predetermined distance, a flat tube in which a plurality of refrigerant flow holes through which a refrigerant flows is formed between the pair of headers, and between the adjacent flat tubes A heat exchanger having fins arranged therein, wherein the header has a structure capable of partitioning the flow of the refrigerant, and when the heat exchanger is used as a condenser, the refrigerant is first The number of the flat tubes flowing into the tube is configured to be in a range of 2.5 to 4.5 times the number of the flat tubes from which the refrigerant finally flows out.

  Further, in the heat exchanger, when two refrigerant flow passages are formed and used as a condenser, the positions of the flat tubes into which the refrigerant first flows are the opposite ends of the header, and the flat tubes from which the refrigerant flows out last. Is at the center of the header.

  Further, the heat exchanger is configured such that the refrigerant first flows in only one of the pair of headers and flows out last.

  In the heat exchanger, the number of the flat tubes into which the refrigerant first flows in from the header is configured to change approximately geometrically before the last outflow.

  When the heat exchanger of the present invention is used as an evaporator or a condenser, the heat exchanger is effectively used for heat exchange by optimizing the number of tubes, so that the heat exchanger does not require a complicated configuration. It is possible to provide a heat exchanger that can maximize the exchange performance and realize high-efficiency operation of the refrigeration cycle system.

  According to a first aspect of the present invention, there is provided a pair of headers extending at a predetermined distance, a flat tube in which a plurality of refrigerant flow holes through which a refrigerant flows is formed between the pair of headers, and the adjacent flat pieces. A heat exchanger having fins disposed between pipes, wherein the header has a structure capable of partitioning the inflow and outflow of the refrigerant, and when the heat exchanger is used as an evaporator, By configuring the number of the flat tubes from which the refrigerant flows out last to be in a range of 1 to 2.5 times the number of the flat tubes from which the refrigerant first flows in, the pressure loss of the refrigerant is low, Highly efficient heat exchange can be performed.

  According to a second aspect of the present invention, there is provided a pair of headers extending at a predetermined distance, a flat tube in which a plurality of refrigerant flow holes through which a refrigerant flows is formed between the pair of headers, and the adjacent flat pieces. A heat exchanger having fins arranged between pipes, wherein the header has a structure capable of partitioning the inflow and outflow of the refrigerant, and when the heat exchanger is used as a condenser, By arranging so that the number of the flat tubes into which the refrigerant first flows in is in a range of 2.5 to 4.5 times the number of the flat tubes through which the refrigerant finally flows out, As the refrigerant flow rate of the supercooled liquid increases, the heat transfer coefficient of the refrigerant is improved, and the refrigerant and air can effectively exchange heat.

  According to a third aspect of the present invention, in the heat exchanger, when two refrigerant flow passages are configured and used as a condenser, the positions of the flat tubes into which the refrigerant first flows are at both ends of the header. By arranging the outlet flat tube so that it is in the center of the header, the condenser outlet close to the refrigerant temperature approaches, so even if it is composed of two refrigerant flow passages, it is optimal and highly efficient Heat exchange can be performed.

  According to a fourth aspect of the present invention, in the heat exchanger, the refrigerant flows in only at one side of the pair of headers and flows out at the end, whereby the inlet / outlet piping of the heat exchanger is arranged on one side. As a result, the length of the piping for routing the piping of the entire system is shortened, so that a reduction in the pressure loss of the refrigerant as the refrigeration cycle system can be reduced.

  According to a fifth aspect of the present invention, the heat exchanger is most optimally arranged by changing in an approximately geometric series before the number of the flat tubes into which the refrigerant first flows in from the header finally flows out. Can perform highly efficient heat exchange.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.

(Embodiment 1)
FIG. 1 is a schematic front view of a parallel flow heat exchanger according to a first embodiment of the present invention.

  In FIG. 1, reference numeral 1 denotes a flat tube through which refrigerant passes. Both ends of the flat tube 1 are inserted into left and right headers 3, 4 so that the refrigerant can smoothly pass through the flat tube 1. . Reference numeral 2 denotes a fin for promoting heat exchange between the refrigerant and air. The left and right headers 3 and 4 have a hollow cylindrical shape, the lower portion of the left header 3 is closed, the upper portion is provided with a connecting pipe 5 led to the refrigeration cycle, and the upper portion of the right header 4 is closed. The lower part is provided with a connecting pipe 6 led from the refrigeration cycle. When used as an evaporator, gas-liquid two-phase refrigerant gas flows from the connecting pipe 6 below the header 4 and evaporates while exchanging heat with the air side through the fins 2 that are in close contact with the flat pipe 1 in the middle. Then, it gasifies and flows out from the connection pipe 5 at the top of the left header 3 to the refrigeration cycle.

Here, the partition plates 7 and 8 are installed inside the left and right headers 3 and 4, respectively, thereby dividing the inside of the left and right headers 3 and 4 into two chambers. Therefore, these partition plates 7 and 8 are divided into a pipe group C (evaporator inlet), a pipe group B (evaporator center), and a pipe group A (evaporator outlet) constituting the group of flat tubes 1. Therefore, the refrigerant flowing into the right header 4 from the connection pipe 6 is once blocked by the partition plate 8 inside the right header 4 and passes through the pipe line group C communicating with the left header 3 to evaporate in FIG. As shown in the schematic diagram showing the flow of the refrigerant in the vessel, the pipe groups B and A meander and flow in an S shape.

  As described above, in the process of evaporating and gasifying the refrigerant in the evaporator, the pressure loss of the refrigerant in the pipe increases with an increase in the specific volume of the refrigerant. Further, if the number of the flat tubes 1 of the pipe group A in which the specific volume is large and the pressure loss is likely to increase is increased in order to reduce the pressure loss, the heat transfer coefficient of the refrigerant also decreases as the refrigerant flow rate decreases, and heat is increased. Since the evaporator capacity Q of the exchanger is also reduced, the optimum of the pipe line group C on the refrigerant inlet side of the evaporator having a small specific volume and a small pressure loss so that the performance of the heat exchanger can be maximized. And the optimum design of the number of flat tubes 1 in the tube group A at the outlet of the evaporator (the ratio of the number of flat tubes A / C) is required. Therefore, FIG. 3 shows the relationship between the evaporator capacity Q and the ratio of the number of flat tubes 1 of the evaporator (group A / group C) obtained from the experimental results when the test was performed in an actual refrigeration cycle system. The performance curve is shown. From the results of the system experiment shown in FIG. 3, the ratio of the number of flat tubes 1 of the evaporator (Group A / Group C) is highest between about 1 and 2.5, and the evaporator capacity Q is about 3000 (kcal / h). It turns out that it becomes the above.

  Therefore, by designing the heat exchanger in consideration of the number of flat tubes so that the ratio of the number of flat tubes in the evaporator (Group A / Group C) is about 1 to 2.5, the heat using the flat tubes Even when the exchanger is used as an evaporator, the evaporation performance can be maximized, and at the same time, the performance of the entire refrigeration cycle system can be improved.

(Embodiment 2)
FIG. 4 is a schematic diagram showing the flow of refrigerant in the heat exchanger indicated by solid arrows when the parallel flow heat exchanger according to the second embodiment of the present invention shown in FIG. 1 is used as a condenser. .

  The contents and principles that are the same as those in the above embodiment are omitted, and the same numbers are used in the following description to indicate the same functions.

  In FIG. 4, high-temperature and high-pressure refrigerant gas discharged from a compressor (not shown) in the refrigeration cycle flows from the connection pipe 5 at the top of the header 3 in FIG. The air is condensed and liquefied while exchanging heat with the air side, and flows out to the refrigeration cycle through the connection pipe 6 below the right header 4.

  Here, the inside of the left and right headers 3 and 4 is divided into two chambers by the partition plates 7 and 8 installed inside the left and right headers 3 and 4. These partition plates 7 and 8 are divided into a pipe group A (condenser inlet), a pipe group B (condenser center), and a pipe group C (condenser outlet) constituting the group of flat tubes 1. Therefore, the refrigerant flowing into the left header 3 from the connection pipe 5 is once blocked by the partition plate 7 inside the left header 3, passes through the pipe line group A communicating with the right header 4, and the partition plate inside the right header 4. 8, the pipe groups B and C meander and flow in an S-shape.

As described above, in the process where the refrigerant is condensed and liquefied by the condenser, the pressure loss of the refrigerant in the pipe line is reduced along with the reduction of the specific volume of the refrigerant. Moreover, if the number of the flat tubes 1 in the conduit group C at the outlet of the condenser through which the refrigerant having an extremely small specific volume passes is extremely reduced, the pressure loss may be increased. If the number of the flat tubes 1 of the pipe group A having a large volume and a large pressure loss is increased to reduce the pressure loss, the heat transfer coefficient of the refrigerant is lowered with a decrease in the flow velocity of the refrigerant. Since the condenser capacity Q is also reduced, the pipe group A on the refrigerant inlet side of the condenser having a large specific volume and a large pressure loss and the condenser outlet so that the performance of the heat exchanger can be maximized. The optimum design of the pipe group C (the ratio of the number of flat pipes A group / C group) is required. Therefore, FIG. 5 shows the performance representing the relationship between the capacity Q of the condenser and the ratio of the number of the flat tubes 1 of the condenser (group A / group C) obtained from the experimental results of tests performed in an actual refrigeration cycle system. A curve is shown. From the results of the system experiment shown in FIG. 5, the ratio of the number of flat tubes 1 of the condenser (Group A / Group C) is highest between about 2.5 and 4.5, and the condenser capacity Q is about 4000 (kcal / h) It turns out that it becomes more than.

With the configuration of the second embodiment, heat exchange is performed in view of the number of flat tubes 1 so that the ratio of the number of flat tubes 1 of the condenser (group A / group C) is about 2.5 to 4.5. By designing the condenser, it is possible to maximize the condensing performance even when the heat exchanger using the flat tube 1 is used as a condenser, and at the same time improve the performance of the entire refrigeration cycle system. .
(Embodiment 3)
FIG. 6 is an experimental result in an actual refrigeration cycle system when the parallel flow heat exchanger according to the third embodiment of the present invention shown in FIG. 1 is used simultaneously for an evaporator and a condenser.

  The contents and principles that are the same as those in the above embodiment are omitted, and the same numbers are used in the following description to indicate the same functions.

  From FIG. 6, the performance curve showing the relationship between the heat exchanger capacity Q of the condenser and the evaporator obtained from the experimental results and the number ratio (group A / group C) of the flat tubes 1 is shown on the same graph. From the results of the system experiment shown in FIG. 6, when the ratio of the number of flat tubes 1 of the heat exchanger (group A / group C) is about 1.5 to 3.5, it is used as an evaporator and a condenser at the same time. Heat exchanger capability Q is high and can be used most effectively.

  With the configuration of the third embodiment, heat exchange is performed in view of the number of flat tubes so that the ratio of the number of flat tubes 1 of the heat exchanger (group A / group C) is about 1.5 to 3.5. By designing the heat exchanger, it is possible to maximize the heat exchanger performance even when the heat exchanger using the flat tube 1 is used as an evaporator and a condenser, and at the same time improve the performance of the entire refrigeration cycle system Can be planned.

  In the first to third embodiments, the partition plates 7 and 8 are installed inside the left and right headers 3 and 4 and the refrigerant passage is configured to meander twice and flow through the heat exchanger. However, the number of partition plates is further increased. Even if it is configured to meander three or more times, it has the same meaning as in the above embodiment, and also has the same meaning in a form in which the flat tubes 1 are arranged vertically with the left and right headers 3 and 4 in the horizontal direction. Is.

(Embodiment 4)
FIG. 7: is a schematic front view of the parallel flow type heat exchanger concerning Embodiment 4 of this invention.

  The contents and principles that are the same as those in the above embodiment are omitted, and the same numbers are used in the following description to indicate the same functions.

In FIG. 7, the partition plates 11 and 13 are respectively arranged at the center of the left and right headers 3 and 4, and the left and right headers 3 and 4 are divided into an upper part and a lower part from the center. Partition plates 12 and 14 are installed, and connecting pipes 15 and 16 to the refrigeration cycle are installed vertically in the center of the right header 4. Therefore, for example, the refrigerant flow when used as a condenser will be described below with reference to the schematic diagram showing the refrigerant flow at the time of condensation in FIG. 8. The refrigerant was discharged from a compressor (not shown) in the refrigeration cycle. High-temperature and high-pressure refrigerant gas flows from the upper and lower connecting pipes 9 and 10 of the right header 4 and condenses, liquefies, and dissipates heat while exchanging heat with the air side through the fins 2 that are in close contact with the flat pipe 1. The refrigerant having a low temperature is concentrated in the center of the right header 4 and has two refrigerant distribution paths that flow out from the two places of the connecting pipes 15 and 16 to the refrigeration cycle, and is used as an evaporator. In this case, the flow is opposite to the flow of the condenser.

  Here, the inside of the left header 3 is divided into two chambers and the inside of the right header 4 is divided into four chambers by the partition plates 11, 12, 13, and 14 installed inside the left and right headers 3 and 4. Pipe group D (upper condenser inlet), pipe group E (upper condenser outlet), and pipe group F (which constitutes a group of flat tubes 1 divided by these partition plates 11, 12, 13, 14 Since the refrigerant flow is divided into a lower condenser outlet) and a pipe line group G (lower condenser inlet), as shown in FIG. The partition plates 12 and 14 meander and flow through the pipe line groups D to E and G to F.

  If it is the structure of this Embodiment 4, high temperature refrigerant gas will be inserted from the upper and lower positions, and the low temperature refrigerant | coolant cooled by air and heat exchange will be collected in the center, and refrigerant | coolants from which temperature differences differ Again, heat exchange is not wasted in the heat exchanger, and even when the heat exchanger using the flat tube 1 is used as a condenser, it is possible to maximize the condensing performance, and at the same time freezing The performance of the entire cycle system can also be improved.

  In the above embodiment, the partition plates 11, 12, 13, and 14 are installed inside the left and right headers 3 and 4, and the refrigerant passage that flows through the heat exchanger by meandering once is configured. Even if it is configured to meander twice or more, it has the same meaning as in the above embodiment, and also in the form in which the left and right headers 3 and 4 are in the horizontal direction and the flat tubes are arranged vertically, it has the same meaning. is there.

  The same effect can be obtained even when the partition plates 11 and 13 inside the left and right headers 3 and 4 are not installed.

(Embodiment 5)
FIG. 9 is a schematic front view of a parallel flow heat exchanger according to a fifth embodiment of the present invention.

  The same content as the above embodiment is simplified or omitted, and the same number will be described below if it shows the same function.

  In FIG. 9, the left header 3 is divided into two chambers and the right header 4 is divided into three chambers by partition plates 17, 18, and 19 installed inside the left and right headers 3 and 4. At the time of condensation, the group of each flat tube 1 of the parallel flow type heat exchanger constituted by the total number of 30 flat tubes 1 by these partition plates 17, 18, 19 is connected to a pipe group H (condenser inlet). ), Pipe group I (condenser center upper part), pipe group J (condenser center lower part) and pipe group K (condenser outlet), for example, the flow of refrigerant as a condenser The high temperature and high pressure refrigerant gas discharged from the compressor (not shown) in the refrigeration cycle is transferred from the connection pipe 9 to the right header 4 with reference to the schematic diagram showing the flow of the refrigerant during condensation in FIG. The refrigerant flowing in is temporarily blocked by the partition plate 18 inside the right header 4, passes through the pipe group H communicating with the left header 3, and the pipe group I by the partition plates 17 and 19 inside the left and right headers 3 and 4. , J meanders into an S-shape, and finally passes through the conduit group K to condense and liquefy. Refrigerant flowing in the refrigeration cycle from the connection pipe 10. Here, as described in the above embodiment, when a parallel flow type heat exchanger is used in a condenser or an evaporator, a pipe group H on the refrigerant inlet side during condensation and a pipe line on the condenser outlet As described above, the optimum design of the group K (flat tube H group / number ratio of the K group) is required, and further, each pipe group H when considered as a whole heat exchanger, An optimal design of I, J, and K is also required. In particular, in the case of a refrigerant passage configuration that repeats meandering three or more times as shown in FIG. 9, it is also necessary to optimize the middle pipe groups I and J.

Therefore, in the case of a parallel flow type heat exchanger composed of 30 flat tubes 1, the flat tubes 1 are arranged from the tube group H at the condenser inlet toward the tube group K in consideration of the overall balance. The number of pipe groups H is fixed to N (for example, eight) and the number of pipe groups I is fixed to M (for example, six) so that the number of pipes is reduced. When the number of the outlet pipe line groups K was arbitrarily changed and tested in the refrigeration cycle system, the results shown in FIG. 11 were obtained.

  Therefore, from this experimental result, the ratio of the number of flat tubes 1 at the condenser inlet / outlet is condensed. The condenser is most suitable when it is designed to apply to about 2.5 to 4.5 (HI-J-K = 13-8-6-3 or 12-8-6-4). Ability Q is high.

  If it is the structure of this Embodiment 5, in consideration of the balance of the whole heat exchanger, the heat exchanger which used the flat tube 1 is designed by designing the heat exchanger which optimized the number of the flat tubes 1 of each pipe line group. Even when the exchanger is used as an evaporator and a condenser, it is possible to maximize the performance of the heat exchanger, and furthermore, connecting pipes 9 and 10 through which refrigerant from the refrigeration cycle flows in and out are only provided on one side header. The installation eliminates the need for extra connection piping from the heat exchanger to the refrigeration cycle. In addition, the apparatus can be miniaturized and the performance of the entire refrigeration cycle system can be improved.

  In each of the above embodiments, a flat tube is used. Therefore, even if the tube thickness is the same, the tube diameter is small, so that the pressure resistance is increased. A heat exchanger of the form is effective.

  Further, since the volume of the flat tube is small, the amount of refrigerant can be reduced, and when using HC refrigerant or the like that is a combustible refrigerant, the heat exchangers of the above embodiments are effective.

  As described above, when the heat exchanger using the flat tube according to the present invention is optimally designed and used, the heat exchange performance can be maximized without requiring a complicated configuration. It can also be applied to heat exchangers such as air conditioners and car air conditioners.

1 is a schematic front view of a parallel flow heat exchanger according to Embodiment 1 of the present invention. The schematic diagram which shows the flow of the refrigerant | coolant in the evaporator in Embodiment 1 of this invention. The figure showing the relationship between the evaporator capability Q and the number ratio (A group / C group) of the flat tubes of an evaporator in Embodiment 1 of this invention. The schematic diagram which shows the flow of the refrigerant | coolant in the condenser in Embodiment 2 of this invention. The figure showing the relationship between the condenser capacity Q in Embodiment 2 of this invention, and the number ratio (A group / C group) of the flat tubes of a condenser. The figure showing the relationship between the heat exchanger capacity Q of the evaporator and the condenser in Embodiment 3 of this invention, and the number ratio (A group / C group) of the flat tube of a heat exchanger. Schematic front view of a parallel flow heat exchanger according to a fourth embodiment of the present invention. The schematic diagram which shows the flow of the refrigerant | coolant in the condenser in Embodiment 4 of this invention. Schematic front view of a parallel flow heat exchanger according to Embodiment 5 of the present invention The schematic diagram which shows the flow of the refrigerant | coolant in the condenser in Embodiment 5 of this invention. The figure showing the relationship between the condenser capacity | capacitance Q in Embodiment 5 of this invention, and the number change of the flat tube of each pipe line group (HI). Schematic front view of a conventional parallel flow heat exchanger Schematic showing the refrigerant flow in the evaporator in a conventional parallel flow heat exchanger Schematic diagram showing the refrigerant flow in the condenser in a conventional parallel flow heat exchanger

Explanation of symbols

1 Flat tube 2 Fin 3 Left header 4 Right header 5, 6, 9, 10, 15, 16 Connection tube 7, 8, 11, 12, 13, 14, 17, 18, 19 Partition plate A, D, G, H Condenser inlet or evaporator outlet group B, I, J Condenser center or evaporator center group C, F, E, K

Claims (5)

A pair of headers extending at a predetermined distance, a flat tube in which a plurality of refrigerant flow holes through which a refrigerant flows are formed between the pair of headers, and the adjacent flat tubes are disposed. A heat exchanger having fins, wherein the header has a structure capable of partitioning the inflow and outflow of the refrigerant, and when the heat exchanger is used as an evaporator, the refrigerant flows out last. The heat exchanger is configured such that the number of the flat tubes is in a range of 1 to 2.5 times the number of the flat tubes into which the refrigerant first flows. A pair of headers extending at a predetermined distance, a flat tube in which a plurality of refrigerant flow holes through which a refrigerant flows are formed between the pair of headers, and the adjacent flat tubes are disposed. The header has a structure that can partition the flow of the refrigerant inside the header, and when the heat exchanger is used as a condenser, the refrigerant flows first. The heat exchanger is configured so that the number of the flat tubes is 2.5 to 4.5 times the number of the flat tubes from which the refrigerant finally flows out. In the heat exchanger, when two refrigerant flow passages are configured and used as a condenser, the positions of the flat tubes into which the refrigerant first flows are the opposite ends of the header, and the positions of the flat tubes from which the refrigerant flows out last. The heat exchanger according to claim 2, wherein is at the center of the header. The heat exchanger according to any one of claims 1 to 3, wherein the heat exchanger is configured such that the refrigerant first flows in only one of the pair of headers and flows out last. 5. The heat exchanger according to claim 1, wherein the number of the flat tubes into which the refrigerant first flows in from the header is configured to change approximately geometrically before the last flow out. The heat exchanger of any one of Claims.

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