JP2001141379A - Compound heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compound heat exchanger that composes a series of refrigerant circuits over all modules while a plurality of heat exchanger modules are arranged in parallel overlappingly and has low pressure loss at a refrigerant side. SOLUTION: The heat exchange pipes of heat exchange modules M1-M3 consist of flat tubes 3... where flat surfaces are arranged opposing. The flat tube 3 of a module being located at the side of higher dryness of a refrigerant corresponding to a flow direction (a) of air is provided with tube width w3 that is larger than that of the flat tube 3 of a module being located at a side with lower dryness.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a double heat exchanger used for an evaporator and a condenser in an air conditioner system for automobiles, home use, business use, and the like.

[0002]

2. Description of the Related Art As a heat exchanger of an air conditioner system, a number of flat tubes forming a heat exchange conduit are connected in parallel to both header tanks at both ends thereof, and are arranged in parallel between a pair of opposed header tanks. A stacked heat exchanger is generally used, which constitutes a part and has meandering fins interposed between adjacent flat tubes. And especially in the evaporator, such a stacked heat exchanger is used as a heat exchange module, and a plurality of the heat exchange modules are arranged in parallel in an overlapping manner to form a series of heat exchange circuits over all modules. Vessels are heavily used.

FIG. 9 shows three heat exchange modules (M1).
A configuration example of a conventional dual heat exchanger composed of (M2) and (M3) is shown. Heat exchange module (M1) for this double heat exchanger
(M3) are a pair of upper and lower round pipe-shaped header tanks (21) and (22), and a large number of flattened core parts (20) arranged in parallel between both header tanks (21) and (22). It has the same structure and size consisting of tubes (23) ..., and allows the adjacent header tanks (21) (21) and (22) (22) to communicate (not shown) at appropriate places. It constitutes a series of refrigerant circuits. (24) is a meandering fin interposed between adjacent flat tubes (23) and (23).
5) are covers arranged on both sides of the core portion (20). Both of the covers use a wide member as a common member covering all the parallel modules (M1) to (M3), and the modules (M1) to (M1). In some cases, a narrow member as an independent member corresponding to each of (M3) is used.

By the way, in this type of double heat exchanger, in order to obtain high heat exchange efficiency, it is general to set a refrigerant circuit so that the flow of the refrigerant becomes a cross counter flow in the direction of air flow. It is. That is, in the example of FIG. 9, the refrigerant flows in from the refrigerant inlet (26) provided in the lower header tank (22) of the module (M1), and flows through the core (20) of the module (M1) from below. Flow, then flow from top to bottom through the core (20) of the module (M2), further flow from bottom to top through the core (20) of the module (M3), and finally the upper header tank of the module (M3) The refrigerant flows out from the refrigerant inlet (27) provided in (21), and in this process, each core portion (20) is set to exchange heat with air flowing in the parallel direction of the modules (M1) to (M3).

[0005]

However, when the refrigerant flowing through the refrigerant circuit is a two-phase flow in which a gas phase component and a liquid phase component are mixed, the degree of dryness due to heat exchange (ratio of the gas phase component)
However, in the conventional double heat exchanger, the flow rate of the refrigerant in the core portion is high in the heat exchange module on the side where the dryness is high due to the arrangement relationship with respect to the air flow direction. On the other hand, in the module on the low dryness side, the flow velocity is slowed down, so that there is a problem that the pressure loss on the refrigerant side increases.

SUMMARY OF THE INVENTION In view of the above circumstances, the present invention is a dual heat exchanger in which a plurality of heat exchange modules are arranged in parallel in an overlapping manner to form a series of refrigerant circuits for all modules, and the pressure loss on the refrigerant side is small. Its main purpose is to provide things.

[Means for Solving the Problems]

In order to achieve the above object, a duplex heat exchanger according to the first aspect of the present invention comprises a pair of opposed header tanks and a plurality of heat exchange tubes arranged in parallel with both ends communicating with both header tanks. A flat tube in which these modules are arranged in parallel in an overlapping manner to form a series of refrigerant circuits, and the heat exchange tubes of each heat exchange module are arranged with their flat surfaces facing each other. The flat tube of the module on the side where the dryness of the refrigerant is high corresponding to the flow direction of air has a larger tube width than the flat tube of the module on the side where the dryness is low. .

According to the above configuration, the degree of dryness of the refrigerant flowing through the core of each module can be different depending on the positional relationship with respect to the direction of air flow. In this case, since the cross-sectional area of the flow passage of the heat exchange pipeline is large, and the cross-sectional area of the same flow passage is small in the module on the low dryness side, the flow velocity of the refrigerant in the core portion of each module is equalized, thereby Pressure loss is reduced. However, in a composite heat exchanger including three or more heat exchange modules, the flat tubes having different tube widths for each module are arranged so that the tube width of the flat tubes sequentially increases or decreases from one side of the module array to the other side. May be used.

According to a second aspect of the present invention, in the double heat exchanger of the first aspect, the plurality of heat exchange modules are positioned such that the arrangement direction of the header tanks is oblique to the longitudinal direction of the flat tubes. Are shifted from each other. In this configuration, when the dual heat exchanger is installed in an inclined state with respect to the flow direction of air, if the arrangement direction of the header tank is adjusted to the flow direction of air, the effective flow path of air in the core portion is wide. Become. When each heat exchange module has a structure in which the end of each flat tube is inserted and connected to a pipe-shaped header tank, the header tanks having a larger width (outer diameter) than the flat tubes are connected to each other by a double heat exchanger. The arrangement is such that an overlap occurs in the thickness direction, and the interval between the flat tubes of the adjacent modules is reduced by the overlap, so that the overall composite heat exchanger becomes thin.

According to a third aspect of the present invention, in the double heat exchanger according to the first aspect, a header member is provided which is divided into a plurality of hollow portions whose insides are continuous in the longitudinal direction. It constitutes the header tank of the heat exchange module. In this case, since the header tanks of the plurality of heat exchange modules can be constituted by a single header member, the number of members is reduced, the workability of assembling and manufacturing is improved, and the manufacturing cost is reduced.

According to a fourth aspect of the present invention, in the double heat exchanger of the third aspect, the header member is provided at least in the widest hollow portion between the wall portion on the flat tube connecting side and the wall portion opposed thereto. Are connected to each other, and the spaces on both sides of the intermediate wall are connected to each other through the opening of the intermediate wall. In this case, the portion of the header member having the widest hollow portion is originally weak in strength, but the necessary strength can be secured by reinforcement with the intermediate wall portion.

According to a fifth aspect of the present invention, in the double heat exchanger of any one of the first to fourth aspects, the flat tubes of each heat exchange module are so arranged that the insertion depth into the header tank is sequentially different for each tube. It has been attached to. According to this configuration, in the area where the refrigerant is distributed from the inside of the header tank of each module to each flat tube of the core portion, the difference in the distance between the opening end of each tube and the inlet of the refrigerant to the header tank causes the amount of refrigerant to be distributed. However, the tube farther from the refrigerant inlet can increase the depth of insertion into the header tank, thereby equalizing the amount of refrigerant distribution.

[0013]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of a double heat exchanger according to an embodiment of the present invention. 1 is a first and a second embodiment, FIG. 2 is a third embodiment, FIGS. 3 to 5 are fourth and fifth embodiments, FIGS. 6 and 7 are sixth embodiments, and FIG. 8 is a seventh embodiment. Examples are shown below.

The double heat exchanger of the first embodiment is applied to an evaporator, and as shown in FIGS.
The base heat exchange modules (M1), (M2), and (M3) are arranged in parallel in an overlapping manner and integrated. In each of these modules (M1) to (M3), a number of flat tubes (3) forming a heat exchange conduit are provided between a pair of round pipe-shaped header tanks (1) and (2) opposed to each other. The core portion (10) is configured by arranging the deflected planes in parallel to face each other.
Thus, each flat tube (3) has a slit-shaped opening (1a) in the peripheral surface of both header tanks (1) and (2) at both ends.
(2a). Modules (M1) to (M1) are located between adjacent flat tubes (3) and (3).
A wide meandering fin (4) as a common member extending over 3) is interposed. (5) are covers arranged on both sides of the core (10).

The three modules (M1) to (M3)
The tube width of the flat tube (3) used for each is different. That is, as shown in FIG. 1 (b), the flat tube (3) has the minimum width (w1) of the module (M1) on the leeward side in the air flow direction indicated by the arrow (a).
The intermediate module (M2) has an intermediate width (w2),
The module (M3) on the windward side has the maximum width (w3). According to the difference in the tube width, the diameter of the upper and lower header tanks (1) and (2) is also changed by the module (M
1) is the smallest and the module (M3) is the largest.

As shown in FIG. 1A, the lower header tank (2) of the module (M1) is provided with a refrigerant inlet (6a) and the upper header tank (1) of the module (M3). ) Are provided with refrigerant inlets (6b). Then, the modules (M1) and (M
The upper header tanks (1) and (1) of 2) and the lower header tanks (2) and (2) of the module (M2) and (M3) are connected to each other via a connection pipe (not shown) or the like. The module (M1)
A series of refrigerant circuits in which the flow of the refrigerant becomes a cross counter flow with respect to the flow of the air over (M3).

When the double heat exchanger of the first embodiment is used as an evaporator, the two-phase refrigerant flowing from the refrigerant inlet (6a) has a low dryness with a small proportion of gas phase components at first. Although it is in a state, as shown by an arrow (r) in FIG.
Each of the core portions (10) flows sequentially upward in the module (M1), downward in the module (M2), and upward in the module (M3). In this process, the vaporization heat is taken from the air flowing in the direction of the arrow (a). Since the liquid phase component evaporates, the proportion of the gas phase component gradually increases and finally flows out from the refrigerant outlet (6b) in a state of high dryness.

Although the volume of the two-phase flow refrigerant increases as the degree of dryness increases due to the above heat exchange, the flat tube having the higher degree of dryness (from the module (M1) to (M3)). 3) The larger the tube width and the larger the cross-sectional area of the flow channel, the more the module (M1)-
The flow velocity of the refrigerant in the core part (10) of (M3) is equalized. Therefore, in this duplex heat exchanger, the module (M
The pressure loss on the refrigerant side is reduced as compared with the conventional double heat exchanger having the flat tubes 1) to (M3) having the same tube width.

The double heat exchanger of the first embodiment is applied to an evaporator, and its heat exchange module (M1)
If the relationship of the tube width of the flat tube (3) in (M3) is reversed, a double heat exchanger applied to the condenser is obtained. That is, in the duplex heat exchanger of the second embodiment shown in FIG. 1C, the basic configuration of the heat exchange modules (M1) to (M3) and the configuration of the refrigerant circuit are the same as those of the first embodiment, but are flat. Tube (3) is the leeward module (M1)
Is the maximum width (w3), and the module (M3) on the windward side is opposite to the minimum width (w1). Also, in response to this difference in tube width, the upper and lower header tanks (1) (2)
The maximum diameter of the module (M1) is
3) is the minimum.

When the double heat exchanger of the second embodiment is used as a condenser, the two-phase refrigerant introduced into the lower header tank (2) of the module (M1) initially has a gas phase component. Although the ratio is high and the dryness is large, the latent heat is generated in the air while the cores (10) of the modules (M1) to (M3) sequentially flow in the cross counter flow with respect to the flow of the air as shown by the arrow (r). And the gas phase component is condensed, the proportion of the gas phase component gradually decreases, and flows out of the upper header tank (1) of the module (M3) in a state of low dryness. The refrigerant volume of the two-phase flow decreases with a decrease in the dryness due to the heat exchange.
Since the cross-sectional area of the flow path is also reduced to 3), the flow velocity of the refrigerant in the core portion (10) of the modules (M1) to (M3) is equalized, and the double heat of the conventional configuration is used as in the first embodiment. The pressure loss on the refrigerant side is reduced as compared with the exchanger.

In the first and second embodiments, the diameter of the upper and lower header tanks (1) and (2) of the heat exchange modules (M1) to (M3) corresponds to the difference in the tube width of the flat tube (3). However, the header tanks (1) and (2) are different from the heat exchange module (M1).
(M3) may be the same diameter. Also, the vertical relationship between the first and second embodiments may be reversed, or both header tanks (1)
(2) may be arranged right and left.

The double heat exchanger (A) according to the third embodiment, which is indicated by a solid line in FIG. 2 (a), is designed to be installed in an inclined state with respect to the direction of air flow, and has three heat exchange modules (M1). )
(M3) The configuration of each member and the configuration of the refrigerant circuit are the same as those in the first and second embodiments. In this duplex heat exchanger, the tube widths of the flat tubes (3) of the modules (M1) to (M3) are sequentially different with the module (M1) being the largest and the module (M3) being the smallest. The header tanks (11) and (11) have the same diameter in all the modules (M1) to (M3).

The modules (M1) to (M1)
3) The alignment direction (O) of the header tanks (11)
And the longitudinal direction (P) of the flat tube (3) are arranged so as to be shifted sequentially so that they obliquely intersect at an angle (θ). The header tanks (11) of the modules (M1) to (M3) communicate with each other at important points to constitute a refrigerant circuit of the cross counter flow similar to the first and second embodiments.

The double heat exchanger (A) of the third embodiment is
For example, as shown in FIG. 2 (b), due to spatial restrictions due to the surrounding conditions of the installation site and the like, the installable width (L0) in the direction perpendicular to the air flow direction shown by the arrow (a) is a normal double heat exchange. When the width is less than the full width of the vessel, the header tanks (11) are installed in an inclined state along the direction of air flow as shown by the solid line in the figure. That is, in this installation state, the effective flow path width of the air in the flow direction of the arrow (a) is (L1), and the modules (M1) to (M1)
Since the entire area of each core section (3) of (3) falls within the effective flow path width (L1), high heat exchange efficiency can be secured.

However, like the heat exchanger (B) shown by the phantom line in the figure, the modules (M1) to (M3) change the direction (O) in which the header tanks (11) are arranged between the flat tubes (3). In a normal configuration in which the flat tubes (3) have the same length as the heat exchanger (A) in a normal configuration arranged in parallel so as to be orthogonal to the longitudinal direction, the heat exchanger (A) is within the installable width (L0). In addition, it is necessary to set the inclination tank to a greater degree than the above, and the part where the header tanks (11) of the modules (M1) to (M3) are arranged on the windward side blocks the air flow path. The effective flow path width (L2) of the heat exchanger (A) is much narrower than the effective flow path width (L1) of the heat exchanger (A), and the heat exchange efficiency is reduced.

Further, in the structure in which the modules (M1) to (M3) are sequentially shifted in the longitudinal direction (P) of the flat tube (3) as in the double heat exchanger (A) of the third embodiment. The round pipe-shaped header tanks (11) having a larger width (outer diameter) than the flat tubes (3) are overlapped with each other in the thickness direction of the double heat exchanger.
As compared with a normal configuration in which the positions of the modules (M1) to (M3) do not shift as in the heat exchanger (B) shown by the imaginary line in (A), the adjacent modules (M1) and (M2) The distance between the flat tubes (3) and (3) is (d3) to (d3).
1) and the same interval between the modules (M1) and (M2) is reduced from (d4) to (d2). Therefore, there is an advantage that the overall heat exchanger becomes thinner.

In the third embodiment, the header tanks (11) of the modules (M1) to (M3) are all of the same diameter, but the modules (M1) to (M3) are formed in the longitudinal direction of the flat tube (3). In the configuration in which the positions are sequentially shifted in the direction (P), the header tanks of the modules (M1) to (M3) correspond to the width of the flat tube (3) as in the first and second embodiments. And different diameters.

In assembling and manufacturing the double heat exchanger as in the first to third embodiments, the header tanks (1) and (2) are used.
(11) A brazing sheet is used for components such as the flat tube (3), the meandering fins (4), and the cover (5), or a brazing material is separately provided at a joint between the components,
A method is adopted in which these constituent members are temporarily assembled and integrally joined by brazing in a furnace.

In the duplex heat exchangers of the fourth and fifth embodiments shown in FIGS. 3A and 3B, the header is divided into three hollow portions (7a) to (7c) whose insides are continuous in the longitudinal direction. Using the member (7), each of the hollow portions (7a) to (7c) is used as a header tank (12) of each module (M1) to (M3). Then, the hollow portion (7) of the header member (7)
A communication circuit (not shown) is provided at important points of the partition walls (70) and (70) for partitioning a) to (7c), thereby forming a cross counter flow refrigerant circuit similar to the first to third embodiments. are doing.

The header member (7) is formed of a hollow extruded material, and corresponds to the different tube widths (w4) to (w6) of the flat tubes (3) of the modules (M1) to (M3). 7a) is set to be wide, the hollow portion (7b) is set to have an intermediate width, and the hollow portion (7c) is set to have a narrow width. Each of these (7a) to (7c) has a long side as shown in FIG. Hole-like tube insertion holes (71a) to (71c) are formed at regular intervals in the longitudinal direction.

Thus, in the duplex heat exchanger of the fourth embodiment shown in FIG. 3A, each of the flat tubes 3 of the modules M1 to M3 is connected as shown in FIG. End portions (3a) made of independent tube materials and drawn (sized) are inserted into the tube insertion holes (71a) to (71c) of the header member (7).

On the other hand, in the double heat exchanger of the fifth embodiment shown in FIG. 3B, three flat tubes of different tube widths (w4) to (w6) corresponding to the modules (M1) to (M3) are used. (3) is integrated as one hollow extruded plate member (30) also shown in FIG. The end (3a) of the plate material (30) is drawn (sized) and has a notch (31a) at a flat connecting portion (31) between the adjacent flat tubes (3) and (3). The two notches (31a) and (31a) fit over the respective boundaries between the tube insertion holes (71a) (71b) and (71b) (71c) of the header member (7). And the header member (7)
Are inserted into the tube insertion holes (71a) to (71c).

In the constructions of the fourth and fifth embodiments, three modules (M1) are provided by a single header member (7).
Since the three header tanks (12) of (M3) to (M3) are configured, the number of members is reduced as compared with the case where each header tank is formed of an independent member as in the first to third embodiments, and the assembly and manufacturing process is reduced. There is an advantage that workability is improved and manufacturing cost is reduced. In addition, the round pipe-shaped header tank used in the first to third embodiments is often manufactured by pressing a brazing sheet into a cylindrical shape, but there is a possibility that defective brazing of the cylindrical seam may occur. In addition, the use of an expensive brazing sheet has the disadvantage that the material cost is high. However, since a hollow extruded material can be used for the header member (7), there is no fear of refrigerant leakage as described above, and the material cost is also low. Can save money.

Further, according to the configuration of the fourth embodiment, since the ends (3a) of the flat tubes (3) are drawn, the flat tubes (3) (3) of the modules (M1) to (M3) are mutually formed. 3) The gap (d) between them can be made very small, and the gap (d) can be made zero depending on the degree of the drawing process, thereby facilitating the thinning of the dual heat exchanger. Further, in the configuration of the fifth embodiment, the number of members is further reduced as compared with the case of the fourth embodiment, so that the workability of assembling and manufacturing is further improved.

In the production of the composite heat exchangers of the fourth and fifth embodiments, a method of integrally joining together by brazing in a furnace in a state where the constituent members are temporarily assembled is also adopted. In this case, the joining of the header member (7) and the flat tubes (3)... Or the plate members (30) of the modules (M1) to (M3) is performed as shown in FIG. Tube insertion holes (8a) corresponding to the tube insertion holes (71a) to (71c) on the joint side surface.
What is necessary is just to arrange | position the brazing sheet (8) which has-(8c), and to perform the said brazing in a furnace. As a result, the amount of expensive brazing sheet used can be minimized, and material costs can be reduced. Instead of using the brazing sheet (8), a brazing material layer may be formed by spraying a brazing material on the joint side surface of the header member (7), and this method further reduces the material cost. It becomes possible.

The dual heat exchanger of the sixth embodiment shown in FIG.
It is composed of two heat exchange modules (M1) and (M2), but is divided into two hollow portions (90) and (91) that are continuous in the longitudinal direction as in the fourth and fifth embodiments. Using the header member (9), each of the hollow portions (90) and (91) is connected to the header tank (13) of the module (M1) (M2).
And Elongated tube insertion holes (92a) (92b) are provided at regular intervals on one side of both hollow portions (90) (91) of the header member (9). (92a) and (92b) have different tube widths (w7) of both modules (M1) and (M2).
The drawn end (3a) of each flat tube (3) having (w8) is inserted.

However, in this header member (9),
A wide hollow portion (90) corresponding to the module (M1) side having a large tube width (w7) connects a flat tube connecting side wall portion (90a) and a wall portion (90b) opposed thereto. Having an intermediate wall (93) and the intermediate wall (93);
Are connected to the intermediate wall (93) by openings (93a) provided at regular intervals. Therefore, the header member (9) is provided with a strength capable of sufficiently withstanding as a header tank as a whole, a portion having a wide hollow portion (90) which is weak in strength is reinforced by the intermediate wall portion (93). I have.

To manufacture such a header member (9), as shown in FIG. 7, the header member (9) is connected to an inner frame (9a) on the flat tube connecting side and an outer frame on the non-connecting side. (9b) and the two frames (9a) and (9b).
Is manufactured from an extruded mold, and tube insertion holes (92a) and (92b) are formed in the extruded mold to be used as the inner frame (9a).
A convex strip (94) provided on an extruded die material to be an outer frame (9b)
By cutting out the important points (1) and (2), the intermediate wall (93) and the opening (93a) thereof are formed, and then both (9a) and (9b) may be joined and integrated by welding or brazing. The dividing shape when dividing the header member (9) into the two frames (9a) and (9b) can be variously set other than shown, and the intermediate wall portion (93) can be set on the side of the inner frame (9a). The two frame bodies (9a) and (9b) may be manufactured from the same extruded material as a configuration in which the header member (9) is equally divided into two in the thickness direction.

In the above-described sixth embodiment, a double heat exchanger composed of two heat exchange modules (M1) and (M2) has been described as an example. Even when a header member is used, an intermediate wall portion may be provided in a wide hollow portion to reinforce the hollow portion. Further, the intermediate wall portion is not limited to the hollow portion having the widest width, and may be provided in a plurality or all of the hollow portions.

When the refrigerant flows as a two-phase flow through each heat exchange module in the double heat exchanger, gas-liquid separation easily occurs in the header tank due to a difference in density and a difference in velocity between the gas phase component and the liquid phase component. For this reason, the distribution amount of the refrigerant from the inside of the header tank to the flat tubes becomes uneven, and it tends to be difficult to obtain the amount of heat exchange that should occur originally. Therefore, as a measure for suppressing the above-mentioned gas-liquid separation, the structure of the seventh embodiment shown in FIG. 8 is recommended. The structure of the seventh embodiment can be applied to each of the heat exchange modules (M1) to (M3) of the duplex heat exchanger of the first to sixth embodiments described above.

That is, as shown in FIG. 8, in each heat exchange module (M) of the composite heat exchanger of the seventh embodiment, both ends are communicated with a pair of header tanks (14) and (15) and arranged in parallel. The number of flat tubes (3) is the insertion depth (h1) of the end into the header tank (14) on the refrigerant inflow side.
Are set so as to gradually become deeper as the distance from the refrigerant inlet (14a) at one end of the tank increases. Since the flat tubes (3) have the same length, the insertion depth (h2) of the end into the header tank (15) on the refrigerant outflow side is determined by the refrigerant inlet (14a). ) Is deeper as the distance from the refrigerant outlet (15b) at the diagonal position increases. That is, (h1) + (h2) is constant in all the flat tubes (3). (16) in the figure is a cap for sealing both ends of both header tanks (14) and (15).

According to the configuration of the seventh embodiment, the flat tube (3) that is originally farther from the refrigerant inlet (14a) is more difficult for the refrigerant to flow in.
Header tank (14) by flat tubes (3) ... that increase insertion depth (h1) with distance from a)
Since the refrigerant flow path in the inside is narrowed, the pressure of the refrigerant in the direction of the arrow (r) does not decrease, and gas-liquid separation due to the density difference and the speed difference between the gas phase component and the liquid phase component becomes difficult to occur. As a result of the refrigerant being evenly distributed to all the flat tubes (3), high heat exchange efficiency can be obtained. In this case, since the flat tubes (3) can have the same length, the insertion depth (h1) is sequentially changed, but this does not increase the number of parts, and is advantageous in the production and management of members. And
When assembling and manufacturing the heat exchanger, there is no concern that the assembling order of the flat tubes (3)...

The refrigerant inlet (14a) of the header tank (14) may be provided in the middle of the tank or at a plurality of locations. In these cases, the refrigerant inlet (14
The insertion depth of the flat tubes (3)... may be set to be sequentially different (the insertion depth increases as the distance increases) based on the position a).

In the above embodiment, a double heat exchanger constituted by two or three heat exchange modules has been exemplified. However, the present invention is also applicable to a double heat exchanger comprising four or more heat exchange modules. is there. The cross-sectional shape of the header tank in each module, the number of flat tubes,
The design of the detailed configuration such as the ratio of the width of the flat tube between the modules, the structure and position of the refrigerant outlet, the refrigerant circuit configuration, and the like can be variously changed in addition to the embodiment.

[0045]

According to the first aspect of the present invention, a plurality of heat exchange modules are arranged in parallel in an overlapping manner to constitute a series of refrigerant circuits over all the modules. Since the width of the flat tube is larger in a module having a higher degree of dryness of the refrigerant, a module having a smaller pressure loss on the refrigerant side is provided.

According to the second aspect of the present invention, as the above-mentioned multiple heat exchanger, the plurality of heat exchange modules are displaced so that the arrangement direction of the header tanks is oblique to the longitudinal direction of the flat tubes. When the heat exchanger needs to be installed inclined with respect to the air flow direction due to space restrictions due to the surrounding conditions of the installation site, the air passing through the core is effective. A flow path width can be widened and a heat exchanger suitable for thinning as a whole of a double heat exchanger is provided.

According to the third aspect of the present invention, since the header tank of the plurality of heat exchange modules is constituted by a single header member in the above-mentioned multiple heat exchanger, the number of members is small, and the assembly and production are simplified. There is an advantage that workability is improved and manufacturing cost is reduced.

According to the fourth aspect of the present invention, in the double heat exchanger using the above header member, the intermediate wall portion is provided in the wide hollow portion of the header member. There is an advantage that the part is reinforced and required strength as a header tank can be secured.

According to the fifth aspect of the present invention, since the flat tubes of each heat exchange module are mounted so that the insertion depth into the header tank is sequentially different for each tube as the above-mentioned double heat exchanger. In addition, the present invention provides an apparatus in which the amount of refrigerant distributed to a number of flat tubes is equalized, thereby achieving high heat exchange efficiency.

[Brief description of the drawings]

FIG. 1 shows first and second embodiments of the present invention;
(A) is a perspective view of the duplex heat exchanger of the first embodiment, (B)
The figure is a vertical cross-sectional side view of the duplex heat exchanger of the first embodiment without the meandering fins, and the (c) diagram is a vertical cross-sectional view of the double heat exchanger of the second embodiment without the meandering fins. .

FIGS. 2A and 2B show a third embodiment of the present invention, wherein FIG. 2A is a schematic side view of the entire double heat exchanger, and FIG. 2B is a schematic side view of the installed state of the double heat exchanger.

FIGS. 3A and 3B show a fourth embodiment and a fifth embodiment, respectively. FIG. 3A is a longitudinal sectional side view of a main part of the compound heat exchanger of the fourth embodiment with the meandering fins omitted, and FIG. It is a longitudinal section side view of the important section which omits the meandering fin of the compound heat exchanger of a 5th embodiment.

FIGS. 4A and 4B show flat tubes used in the fourth and fifth embodiments. FIG. 4A is a cross-sectional view of the flat tube of the fourth embodiment, and FIG. 4B is a cross section of the flat tube of the fifth embodiment. FIG.

FIG. 5 is a perspective view of a header member and a brazing sheet used in the fourth and fifth embodiments.

FIG. 6 is a vertical sectional side view of a main part of the duplex heat exchanger according to the sixth embodiment, with the meandering fins omitted.

FIG. 7 is a perspective view of an inner frame and an outer frame constituting a header member used in the sixth embodiment.

FIG. 8 is a vertical sectional front view of a heat exchange module in the compound heat exchanger of the seventh embodiment.

FIG. 9 is a perspective view showing a configuration example of a conventional double heat exchanger.

[Explanation of symbols]

 M, M1 to M3: heat exchange module 1, 2, ... header tank 3 ... flat tube 4 ... meandering fin 6a ······· Refrigerant inlet 6b ······· Refrigerant outlet 7 ······ Header member 7a to 7c ······················ ····· Header member 90 ··································································································································· ······ Intermediate wall part 93a ·································································· Header tank Tank arrangement direction P: Longitudinal direction of flat tube a: Air flow direction r: Refrigerant flow ... Tube width h1, h2... Insertion depth

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Toshinori Tokutake 6, 224 Kaiyama-cho, Sakai-shi F-term in Showa Aluminum Co., Ltd. (Reference) 3L103 AA01 AA06 AA11 AA17 AA37 BB38 BB42 CC18 CC30 DD08 DD32 DD34 DD42 DD69

Claims (5)

[Claims] 1. A heat exchange module comprising a pair of header tanks opposed to each other and a plurality of heat exchange tubes arranged in parallel with both ends communicating with both header tanks,
In a composite heat exchanger in which these modules are arranged in parallel in an overlapping manner to form a series of refrigerant circuits, the heat exchange tubes of each heat exchange module are formed of flat tubes with their flat surfaces facing each other, and the air flow direction 2. The double heat exchanger according to claim 1, wherein the flat tubes of the module on the side with the higher dryness of the refrigerant have a larger tube width than the flat tubes of the module on the side with the lower dryness. 2. The heat exchange module according to claim 1, wherein the positions of the header tanks are shifted from each other so that the arrangement direction of the header tanks is oblique to the longitudinal direction of the flat tubes.
The double heat exchanger as described. 3. The dual heat exchanger according to claim 1, further comprising a header member having an interior partitioned into a plurality of hollow portions continuous in the longitudinal direction, wherein each hollow portion of the header member constitutes a header tank of each heat exchange module. Exchanger. 4. The header member has, at least in the widest hollow portion, an intermediate wall portion connecting a wall portion on the flat tube connecting side and a wall portion facing the flat tube connecting side portion, and a space on both sides of the intermediate wall portion. 4. The double heat exchanger according to claim 3, wherein the heat exchanger communicates with an opening of the intermediate wall. 5. The flat tube of each heat exchange module,
The double heat exchanger according to any one of claims 1 to 4, wherein the heat exchanger is mounted so that the insertion depth into the header tank is sequentially different for each tube.