JP2003028583A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger, which has the same performance as the conventional double-pipe heat-exchanger and still in the smallest possible outside shape. SOLUTION: The heat exchanger is composed of a plurality of core pipes 1, 1, etc., arranged parallel in a predetermined length and pipes 2, 2, etc., wound spirally on the outer periphery of the core pipes 1, 1, etc. A continuous duct W is formed by connecting the core pipes 1, 1, etc., by means of core-pipe fittings (e.g. U-shaped joint pipes 3). A continuous refrigerant duct R is formed by connecting the pipes 2, 2, etc., by means of wound pipe fittings 7. Thus, the heat exchanger having the same performance as the conventional double-pipe heat-exchanger can be obtained in a reduced size (e.g. the outside shape).

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchanger for exchanging heat between water and a refrigerant (for example, a water heat exchanger used in a heat pump water heater).

[0002]

2. Description of the Related Art A well-known heat exchanger for a water heater comprises an inner tube through which water flows and an outer tube through which a refrigerant flows, and is bent into an elliptical shape and has a large number of stages. There is a double-tube heat exchanger that is superposed.

In the case of this double-tube heat exchanger, as shown in FIG. 17, in order to stop the operation of the apparatus when a hole is formed in the wall of the inner tube 101 which becomes the water passage W due to corrosion, A leak detection tube 103 having a leak detection groove 102 is provided to detect water leakage promptly. That is, it is substantially configured by a triple pipe including the inner pipe 101, the leak detection pipe 103, and the outer pipe 104.

[0004]

The conventional double-tube heat exchanger described above has the problems that the manufacturing process is complicated and the cost is unavoidably increased. Further, due to the triple tube structure, when the elliptical shape is bent as shown in FIGS. 18 and 19, the radius of curvature of the curved portion B of the heat exchanger A is inevitably large, and the heat exchanger A There is a problem that the inner space portion C becomes large and the outer shape becomes large for the heat exchange capacity.

The present invention has been made in view of the above points, and an object thereof is to make the outer shape of the heat exchanger as small as possible with the performance equivalent to that of the conventional double-tube heat exchanger. To do.

[0006]

According to the invention of claim 1, as means for solving the above-mentioned problems, a plurality of core tubes 1, 1 ... .. and the core tubes 1, 1 ... Connected via a core tube connecting portion to form a series of water passages W. In addition, the winding tubes 2, 2, ... Are connected via a winding tube connecting portion 7 to form a series of refrigerant passages R.

With the above construction, the core tubes 1, 1, ... Which are arranged in parallel and connected by the core tube connecting portions 3, 3, .. The winding tubes 2, 2, ... Wound spirally around the outer circumference of the core tube 1 and connected by the winding tube connecting portion 7 constitute a series of refrigerant passages R. Unlike the heat exchanger, which does not have a space, the size (ie, outer shape) of the heat exchanger can be significantly reduced with the performance equivalent to that of the conventional double-tube heat exchanger.

As in the invention of claim 2, claim 1
In the heat exchanger described in the above, when the core tube connecting portion is composed of a U-shaped connecting tube 3 which is separate from the core tube 1,
A core tube 1 of a predetermined length and a U-shaped connecting tube 3 wrapped around
The heat exchanger can be configured in combination with the above, and a processing space corresponding to the length of the core tube 1 is sufficient in the manufacturing process of the heat exchanger, and space can be saved.

As in the invention of claim 3, claim 1
In the heat exchanger described in the above, when the core tube connecting portion 3 is constituted by the hairpin tube 4 integrated with the core tube 1, the winding tube 2
The heat exchanger can be configured by a combination of the core tube 1 having a predetermined length and the hairpin tube 4 integrated with the core tube 1, and the number of parts can be reduced.

As in the invention of claim 4, claim 1
In the heat exchanger described in the above, when the core tube connecting portion 3 is constituted by a U-shaped passage 5 in a manifold 6, a combination of the core tube 1 and the manifold 6 of a predetermined length around which the winding tube 2 is wound. It becomes possible to configure a heat exchanger with
The number of parts can be reduced.

As in the invention of claim 5, in the heat exchanger according to any one of claims 1, 2, 3 and 4, when the core tubes 1, 1, ... Are arranged on the same plane,
The core tubes 1, 1, ... Arranged on the same plane constitute a heat exchanger, which limits the height dimension.

As in the invention of claim 6, in the heat exchanger according to any one of claims 1, 2, 3 and 4, the core tubes 1, 1, ... Are on the same plane and on the same vertical plane. , The core tubes 1, 1 ... Arranged on the same plane and on the same vertical plane constitute a heat exchanger, and the heat exchanger performance can be greatly improved by a simple method. it can. In other words, the volume of the heat exchanger can be minimized if they exhibit the same performance.

In a seventh aspect of the present invention, as means for solving the above-mentioned problems, a core tube 1 forming a water passage W formed in a spiral shape on the same plane, and a spiral around the outer circumference of the core tube 1. It is constituted by the winding tube 2 which becomes the wound refrigerant passage R.

With the above structure, the core tube 1 formed in a spiral shape on the same plane, and the core tube 1
The heat exchanger is constituted by the winding tube 2 that is spirally wound around the outer circumference of the, and does not have a space portion like the conventional double tube heat exchanger, and thus the conventional double tube The performance (e.g., external shape) of the heat exchanger with the same performance as the heat exchanger
Can be significantly reduced.

As in the invention of claim 8, claim 7
In the heat exchanger described in the above, when a series of water passages W is formed by connecting a plurality of the spiral core tubes 1 to each other, the simple method of stacking a plurality of spiral core tubes 1 is used. The heat exchanger performance can be significantly improved. In other words, the volume of the heat exchanger can be minimized if they exhibit the same performance.

As in the invention of claim 9, in the heat exchanger according to any one of claims 1, 2, 3, 4, 5, 6, 7 and 8, the winding pitch P of the winding tube 2 is When the size is set to be equal to or larger than the predetermined size, when the core tube 1 has a corrosion hole, the leaked water falls from the gap S corresponding to the winding pitch P of the winding tube 2, and the leakage can be detected reliably.

As in the invention of claim 10, in the heat exchanger according to any one of claims 1, 2, 3, 4, 5, 6, 7, 8 and 9, a plurality of the winding tubes 2 are provided. When the main winding is performed at the same time, the refrigerant circulates in a plurality of passes, and the circulation resistance on the refrigerant side can be reduced.

[0018]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Some preferred embodiments of the present invention will be described in detail below with reference to the accompanying drawings.

First Embodiment FIG. 1 shows a heat exchanger according to a first embodiment of the present invention.

This heat exchanger constitutes a water heat exchanger used as a heater in a heat pump water heater, and as shown in FIG. 1, it has a predetermined length and is arranged in parallel on the same plane. A plurality of core tubes 1, 1 ..., and winding tubes 2, 2 ... which are spirally wound around the outer circumference of each core tube 1.
It is composed of and. And the core tube 1, 1
Are connected via U-shaped connecting pipes 3, 3 forming the core pipe connecting part to form a series of water passages W, while the winding pipes 2, 2 ... Are connected to the winding pipe connecting part ( (Integrated with winding tube 2)
Are connected to each other through a series of refrigerant passages R. In this case, a set of two winding tubes 2 and 2 is wound at the same time (in other words, two windings are used), and the winding pitch P of the winding tube 2 is set to a predetermined dimension or more. There is.

In the heat exchanger constructed as described above, the following operational effects can be obtained.

That is, the core pipes 1, 1 ... Connected by U-shaped connecting pipes 3, 3, .. The winding tubes 2, 2, ... Wound in a spiral shape around the core tube 1 and connected by the winding tube connecting portions 7, 7, .. Unlike the double-tube heat exchanger, it does not have a space, and has the same performance as the conventional double-tube heat exchanger, greatly reducing the size (ie, outer shape) of the heat exchanger. be able to.

Moreover, in the case of the heat exchanger according to this embodiment, since the core tube connecting portion is constituted by the U-shaped connecting tube 3 which is separate from the core tube 1, the winding tube 2 It is possible to configure a heat exchanger by combining the core tube 1 of a predetermined length and the U-shaped connecting tube 3 around which is wound, and corresponds to the length of the core tube 1 in the manufacturing process of the heat exchanger. It only needs a processing space, and space can be saved.

Further, since the core tubes 1, 1, ... Are arranged on the same plane, the height dimension is limited.

Further, since the two winding tubes 2 are wound at the same time, the refrigerant flows in a plurality of passes, and the flow resistance on the refrigerant side can be reduced.

By the way, in the present embodiment, since the winding pitch P of the winding tube 2 is set to a predetermined dimension or more,
As shown in FIG. 2, a gap S is formed on the outer periphery of the core tube 1 corresponding to the length obtained by subtracting the diameter of the winding tube 2 from the winding pitch P of the winding tube 2 (in other words, corresponding to the winding pitch P). Will be done. Accordingly, thicker toward the core tube 1 than the thickness t ₁ of the core tube 1 of the wall thickness t ₂ to reach the interior of the winding tube 2, when it is corroded hole in the core tube 1, the winding tube 2 from the core pipe 1 It reaches the outside of the core tube 1 before reaching the inside. As a result, the leaked water falls from the outer circumference of the core tube 1, and the leak can be surely detected.

By the way, if the diameter (outer diameter) of the core tube 1 is too large, the flow velocity of the water W flowing inside decreases, and the heat transfer efficiency decreases. On the contrary, if it is too small, the surface area decreases and the heat transfer efficiency decreases. Or, there is a problem that the pressure loss becomes large. FIG. 3 shows a graph in which the relationship between the outer diameter of the core tube 1 and the hot water temperature is measured under the condition that carbon dioxide (CO ₂ ) is used as the refrigerant and 300 liters of water at 10 ° C. is heated for 6 hours. 4 is a graph in which the relationship between the outer diameter of the core tube 1 and the water side pressure loss is measured under the same conditions as in FIG.

In the case of the present invention, from the above point of view, the outer diameter of the core tube 1 is preferably in the range of 6 mm to 10 mm, but other ranges are not excluded.

On the other hand, as for the outer diameter of the winding tube 2, it is sufficient that the outer diameter of the winding tube 2 is smaller than that of the core tube 1 in view of fin efficiency (heat transfer performance) with the core tube 1. In FIG. 5, the number of windings of the winding tube 2 is 1 to 4
And a graph in which the relationship between the outer diameter of the winding tube 2 and the tapping temperature is measured under the same conditions as in FIG. 3 is shown, and in FIG. 6, under the same conditions as in FIG. The graph which measured the relationship between the winding pitch of the winding tube 2 and the tapping temperature is shown. According to this, the outer diameter of the winding tube 2 is 2 mm to 6 mm.
The winding pitch is preferably in the range of mm, and the winding pitch of the winding tube 2 is preferably in the range of the outer diameter of the winding tube 2 to 12 mm, but the range other than these ranges is not excluded.

Second Embodiment FIG. 7 shows a heat exchanger according to a second embodiment of the present invention.

In this case, the core tube connecting portion for connecting the core tubes 1, 1, ... Is constituted by the hairpin tube 4 integrated with the core tube 1, as shown in FIG. This way,
The heat exchanger can be configured by a combination of the core tube 1 of a predetermined length around which the winding tube 2 is wound and the hairpin tube 4 integrated with the core tube 1, and the number of parts can be reduced. In the case of the heat exchanger according to the present embodiment, since the core tube 1 is considerably long, the step of winding the winding tube 2 around the core tube 1 and bending the core tube 1 to form the hairpin tube. If the process is continuously performed, a very large processing space is not required. Other configurations and effects are the same as those in the first embodiment, and the description thereof will be omitted.

Third Embodiment FIG. 8 shows a heat exchanger according to a third embodiment of the present invention.

In this case, the core tube connecting portion for connecting the core tubes 1, 1 ... Is constituted by the U-shaped passage 5 in the manifold 6, as shown in FIG. In this way, the heat exchanger can be configured by combining the core tube 1 of the predetermined length around which the winding tube 2 is wound and the manifold 6, and the number of parts can be reduced. Moreover, in the manufacturing process of the heat exchanger, it suffices if there is a processing space corresponding to the length of the core tube 1, so that the space can be saved. Other configurations and effects are the same as those in the first embodiment, and the description thereof will be omitted.

Fourth Embodiment FIG. 9 shows a heat exchanger according to a fourth embodiment of the present invention.

In this case, the core tubes 1, 1, ... Are alternately connected by the hairpin tube 4 and the U-shaped connecting tube 3 which constitute the core tube connecting portion, as shown in FIG. With this configuration, the heat exchanger can be configured by a combination of the core tube 1 having the predetermined length around which the winding tube 2 is wound, and the hairpin tube 4 and the U-shaped connecting tube 3 which are integral with the core tube 1. Becomes In this case, the number of U-shaped connecting tubes 3 used can be reduced. Other configurations and effects are the same as those in the first embodiment, and the description thereof will be omitted.

Fifth Embodiment FIG. 10 shows a heat exchanger according to a fifth embodiment of the present invention.

In this case, as shown in FIG.
At one end side (left side in the figure) of the core tube 1, the core tube connecting portion is constituted by the U-shaped passage 5 in the manifold 6, and at the other end side (right side in the figure) of the core tube 1, 1. The core tube connecting portion is composed of a U-shaped connecting tube 3 which is separate from the core tube 1. By doing so, it becomes possible to construct a heat exchanger by combining the core tube 1 of a predetermined length around which the winding tube 2 is wound, the U-shaped connecting tubes 3 and 3, and the manifold 6.
In this case, the number of manifolds 6 or U-type connecting pipes 3 used can be reduced. Other configurations and effects are the same as those in the first embodiment, and the description thereof will be omitted.

Sixth Embodiment FIG. 11 shows a heat exchanger according to a sixth embodiment of the present invention.

In this case, as shown in FIG.
At one end side (left side in the figure) of the core tube 1, the core tube connecting portion is constituted by the U-shaped passage 5 in the manifold 6, and at the other end side (right side in the figure) of the core tube 1, 1. The core tube connecting portion is constituted by the hairpin tube 4 which is integral with the core tube 1. In this way, the heat exchanger can be configured by combining the core tube 1 having the predetermined length around which the winding tube 2 is wound, the hairpin tubes 4 and 4, and the manifold 6.
In this case, the number of manifolds 6 used can be reduced. Other configurations and effects are the same as those in the first embodiment, and the description thereof will be omitted.

Seventh Embodiment FIG. 12 shows a heat exchanger according to a seventh embodiment of the present invention.

In this case, as shown in FIG. 12, the core tube 1,
At one end side (left side in the figure) of the core tube 1, the core tube connecting portion is constituted by the U-shaped passage 5 in the manifold 6, and at the other end side of the core tubes 1, 1 ... The core tube connecting portion is composed of a U-shaped connecting tube 3 which is separate from the core tube 1, and a hairpin tube 4 which is integral with the core tube 1. This makes it possible to construct a heat exchanger with a combination of the core tube 1 around which the winding tube 2 is wound, the U-shaped connecting tube 3, the hairpin tube 4, and the manifold 6. In this case, the number of manifolds 6 or U-type connecting pipes 3 used can be reduced. Other configurations and effects
The description is omitted because it is the same as in the first embodiment.

Eighth Embodiment FIG. 13 shows a heat exchanger according to an eighth embodiment of the present invention.

In this case, three core tubes 1, 1, ... Are arranged on the same plane and two steps are arranged on the same vertical plane, and the core tubes 1, 1 ,. The connecting portion is composed of U-shaped connecting pipes 3, 3, ... Separate from the core pipe 1. By doing so, the heat exchanger is constituted by the core tubes 1, 1, ... Arranged on the same plane and on the same vertical plane, and the heat exchanger performance can be greatly improved by a simple method. it can. In other words, the volume of the heat exchanger can be minimized if they exhibit the same performance. A hairpin tube or a manifold integral with the core tube 1 may be used as the core tube connecting portion. Further, the number of core tubes arranged on the same plane and on the same vertical plane is selected as necessary. Other configurations and effects are the same as those in the first embodiment, and the description thereof will be omitted.

Ninth Embodiment FIG. 14 shows a heat exchanger according to the ninth embodiment of the present invention.

In this case, the heat exchanger is spirally wound around the outer periphery of the core tube 1 and the core tube 1 which is a spiral water passage W formed in a spiral shape on the same plane. And the winding tube 2 serving as the refrigerant passage R. In this case, the heat exchanger is constituted by the core tube 1 formed in a spiral shape on the same plane and the winding tube 2 spirally wound around the outer circumference of the core tube 1. It does not have a space like the heavy-tube heat exchanger, and has the same performance as the conventional double-tube heat exchanger, and the size (ie, outer shape) of the heat exchanger can be greatly reduced. You can In this case, since the radius of curvature of the curved portion can be made relatively large, the flow resistance of the water passage W can be reduced, and adhesion of scale can be suppressed. Further, in the case of the heat exchanger according to the present embodiment, since the core tube 1 is considerably long, the step of winding the winding tube 2 around the core tube 1 and the step of processing the core tube 1 into a spiral shape are consecutive. Then, it does not require a large processing space.

Further, since the core tubes 1, 1, ... Have a spiral shape on the same plane, the height dimension is limited.

Furthermore, since the two winding tubes 2 are wound at the same time, the refrigerant flows in a plurality of passes, and the flow resistance on the refrigerant side can be reduced.

By the way, also in this embodiment, since the winding pitch P of the winding tube 2 is set to a predetermined dimension or more,
As shown in FIG. 2, a gap S corresponding to the length obtained by subtracting the diameter of the winding tube 2 from the winding pitch P of the winding tube 2 is formed on the outer periphery of the core tube 1. Accordingly, thicker toward the core tube 1 than the thickness t ₁ of the core tube 1 of the wall thickness t ₂ to reach the interior of the winding tube 2, when it is corroded hole in the core tube 1, the winding tube 2 from the core pipe 1
It reaches the outside of the core tube 1 before reaching the inside.
As a result, the leaked water falls from the outer circumference of the core tube 1, and the leak can be surely detected.

The spiral shape formed by the core tube 1 may be a shape other than an oval shape (for example, a circular shape, a rectangular shape, an elliptical shape, etc.).

Tenth Embodiment FIGS. 15 and 16 show a heat exchanger according to a tenth embodiment of the present invention.

In this case, as shown in FIGS. 15 and 16, a series of water passages W is constructed by connecting the spirally wound core tubes 1 in an upper and lower two stages (that is, two tubes). ing. Upper core tube 1, lower core tube 1, winding tube 2 wound around upper core tube 1, and lower core tube 1
It is connected to the winding tube 2 wound around the center of the winding tube 2 through connecting portions 8 and 9 at the central portion. By doing so, the heat exchanger performance can be significantly improved by a simple method of stacking the spirally wound core tubes 1. In other words, the volume of the heat exchanger can be minimized if they exhibit the same performance. The spiral core tube 1
The number of overlapping layers is selected as required. Other configurations, functions, and effects are the same as those in the ninth embodiment, so description thereof will be omitted.

[0052]

According to the first aspect of the present invention, a plurality of core tubes 1, 1 ... Having a predetermined length arranged in parallel, and windings spirally wound around the outer circumference of each core tube 1. Tubes 2, 2 ...
, And the core tubes 1, 1, ... Are connected via a core tube connecting portion to form a series of water passages W, and the winding tubes 2, 2 ,. Since the series of refrigerant passages R are connected by way of the above, there is no space portion like the conventional double-tube heat exchanger, and it is equivalent to the conventional double-tube heat exchanger. In terms of performance, there is an effect that the size (that is, outer shape) of the heat exchanger can be significantly reduced.

As in the invention of claim 2, claim 1
In the heat exchanger described in the above, when the core tube connecting portion is composed of a U-shaped connecting tube 3 which is separate from the core tube 1,
A core tube 1 of a predetermined length and a U-shaped connecting tube 3 wrapped around
The heat exchanger can be configured in combination with the above, and a processing space corresponding to the length of the core tube 1 is sufficient in the manufacturing process of the heat exchanger, and space can be saved.

As in the invention of claim 3, claim 1
In the heat exchanger described in the above, when the core tube connecting portion 3 is constituted by the hairpin tube 4 integrated with the core tube 1, the winding tube 2
The heat exchanger can be configured by a combination of the core tube 1 having a predetermined length and the hairpin tube 4 integrated with the core tube 1, and the number of parts can be reduced.

As in the invention of claim 4, claim 1
In the heat exchanger described in the above, when the core tube connecting portion 3 is constituted by a U-shaped passage 5 in a manifold 6, a combination of the core tube 1 and the manifold 6 of a predetermined length around which the winding tube 2 is wound. It becomes possible to configure a heat exchanger with
The number of parts can be reduced.

As in the invention of claim 5, in the heat exchanger according to any one of claims 1, 2, 3 and 4, when the core tubes 1, 1 ... Are arranged on the same plane,
The core tubes 1, 1, ... Arranged on the same plane constitute a heat exchanger, which limits the height dimension.

As in the invention of claim 6, in the heat exchanger according to any one of claims 1, 2, 3 and 4, the core tubes 1, 1, ... Are on the same plane and on the same vertical plane. , The core tubes 1, 1 ... Arranged on the same plane and on the same vertical plane constitute a heat exchanger, and the heat exchanger performance can be greatly improved by a simple method. it can. In other words, the volume of the heat exchanger can be minimized if they exhibit the same performance.

According to the seventh aspect of the present invention, the core tube 1 serving as the water passage W formed in a spiral shape on the same plane,
Since the core tube 1 is constituted by the winding tube 2 which becomes the refrigerant passage R spirally wound around the outer circumference of the core tube 1, it does not have a space portion unlike the conventional double tube heat exchanger, With the same performance as a conventional double-tube heat exchanger, the dimensions of the heat exchanger (ie,
The effect is that the outer shape) can be significantly reduced.

As in the invention of claim 8, claim 7
In the heat exchanger described in the above, when a series of water passages W is formed by connecting a plurality of the spiral core tubes 1 to each other, the simple method of stacking a plurality of spiral core tubes 1 is used. The heat exchanger performance can be significantly improved. In other words, the volume of the heat exchanger can be minimized if they exhibit the same performance.

As in the invention of claim 9, in the heat exchanger according to any one of claims 1, 2, 3, 4, 5, 6, 7 and 8, the winding pitch P of the winding tube 2 is When the size is set to be equal to or larger than the predetermined size, when the core tube 1 has a corrosion hole, the leaked water falls from the gap S corresponding to the winding pitch P of the winding tube 2, and the leakage can be detected reliably.

As in the invention of claim 10, in the heat exchanger according to any one of claims 1, 2, 3, 4, 5, 6, 7, 8 and 9, a plurality of the winding tubes 2 are provided. When the main winding is performed at the same time, the refrigerant circulates in a plurality of passes, and the circulation resistance on the refrigerant side can be reduced.

[Brief description of drawings]

FIG. 1 is a plan view of a heat exchanger according to a first embodiment of the present invention.

FIG. 2 is an enlarged cross-sectional view of the essential parts of the heat exchanger according to the first embodiment of the present invention.

FIG. 3 is a graph showing an example of the relationship between the core tube outer diameter and the tapping temperature in the heat exchanger according to the first embodiment of the present invention.

FIG. 4 is a graph showing an example of a relationship between a core tube outer diameter and a water side pressure loss in the heat exchanger according to the first embodiment of the present invention.

FIG. 5 is a graph showing an example of the relationship between the outer diameter of a winding tube and the outlet heated water temperature in the heat exchanger according to the first embodiment of the present invention.

FIG. 6 is a graph showing an example of the relationship between the winding pitch of the winding tube and the tapping temperature in the heat exchanger according to the first embodiment of the present invention.

FIG. 7 is a plan view of a heat exchanger according to a second embodiment of the present invention.

FIG. 8 is a plan view of a heat exchanger according to a third embodiment of the present invention.

FIG. 9 is a plan view of a heat exchanger according to a fourth embodiment of the present invention.

FIG. 10 is a plan view of a heat exchanger according to a fifth embodiment of the present invention.

FIG. 11 is a plan view of a heat exchanger according to a sixth embodiment of the present invention.

FIG. 12 is a plan view of a heat exchanger according to a seventh embodiment of the present invention.

FIG. 13 is a plan view of a heat exchanger according to an eighth embodiment of the present invention.

FIG. 14 is a plan view of a heat exchanger according to a ninth embodiment of the present invention.

FIG. 15 is a plan view of a heat exchanger according to a tenth embodiment of the present invention.

FIG. 16 is a side view of the heat exchanger according to the tenth embodiment of the present invention.

FIG. 17 is an enlarged perspective view of a main part of a conventionally known double-tube heat exchanger.

FIG. 18 is a plan view of a conventionally known double-tube heat exchanger.

FIG. 19 is a side view of a conventionally known double-tube heat exchanger.

[Explanation of symbols]

1 is a core tube, 2 is a winding tube, 3 is a core tube connecting portion (U-shaped connecting tube),
4 is a core tube connecting portion (hairpin tube), 5 is a core tube connecting portion (U-shaped passage), 6 is a manifold, 7 is a winding tube connecting portion, P is a winding pitch, S is a gap, R is a refrigerant passage, W Is a water passage.

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Haruo Nakata             1304 Kanaoka-cho, Sakai City, Osaka Prefecture Daikin Industries             Sakai Plant Kanaoka Factory F-term (reference) 3L103 AA05 AA35 BB43 CC02 CC12                       DD06 DD08 DD09

Claims (10)

[Claims] 1. A plurality of core tubes (1), (1), ... Arranged in parallel and having a predetermined length, and a winding tube (2) spirally wound around the outer circumference of each core tube (1). ), (2) ... And the core tubes (1), (1) ... Are connected via a core tube connecting portion to form a series of water passages (W),
A heat exchanger characterized in that the winding tubes (2), (2), ... Are connected via a winding tube connecting portion (7) to form a series of refrigerant passages (R). 2. The heat exchanger according to claim 1, wherein the core tube connecting portion is constituted by a U-shaped connecting tube (3) which is separate from the core tube (1). 3. The heat exchanger according to claim 1, wherein the core tube connecting portion is constituted by a hairpin tube (4) integrated with the core tube (1). 4. Heat exchanger according to claim 1, characterized in that the core tube connection (3) is constituted by a U-shaped passage (5) in the manifold (6). 5. The heat exchanger according to claim 1, wherein the core tubes (1), (1), ... Are arranged on the same plane. 6. The core tubes (1), (1), ... Arranged on the same plane and on the same vertical plane according to any one of claims 1, 2, 3 and 4. Heat exchanger. 7. A core tube (1) serving as a water passage (W) formed in a spiral shape on the same plane, and a refrigerant path (R) spirally wound around the outer periphery of the core tube (1). And a wound tube (2) which is 8. The heat exchanger according to claim 7, wherein a series of water passages (W) are formed by connecting a plurality of the spiral core tubes (1) by superimposing them. 9. The winding pitch (P) of the winding tube (2) is set to be equal to or larger than a predetermined dimension.
The heat exchanger according to any one of 2, 3, 4, 5, 6, 7 and 8. 10. The winding tube (2) according to any one of claims 1 and 2, characterized in that a plurality of the winding tubes (2) are wound at the same time.
The heat exchanger according to any one of 3, 4, 5, 6, 7, 8 and 9.