JP2003097898A - Heat exchanger - Google Patents

Abstract

(57) Abstract: In a heat exchanger in which a winding tube is spirally wound around the outer periphery of a core tube, it is possible to suppress adhesion of scale components to the inner wall of the core tube. SOLUTION: A core tube 1 constituting a water passage W, and the core tube 1
And a winding tube 2 spirally wound around the outer periphery of the water passage W to form a refrigerant passage R, wherein the water flowing through the water passage W is heated by the refrigerant flowing through the refrigerant passage R. The winding pitch P 'of the winding tube 2 at the outlet A of the water passage W where the water temperature is equal to or higher than the predetermined temperature is made larger than the winding pitch P on the upstream side of the portion. The amount of heat transferred from the refrigerant flowing in the winding tube 2 to the core tube 1 is reduced.

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 high-temperature refrigerant (for example, a heat exchanger for water used in a heat pump type water heater).

[0002]

2. Description of the Related Art For example, in a heat exchanger for water used in a heat pump type water heater, as the water temperature rises,
Scale components (for example, calcium carbonate) dissolved in water may be deposited and adhere to the inner wall of the water passage. That is, although calcium carbonate is dissolved in tap water,
As can be seen from the solubility curve in FIG. 14, the solubility of calcium carbonate decreases as the water temperature rises, and calcium carbonate precipitates as a scale component. The scale component thus deposited adheres to the inner wall of the water passage. It is known that the adhesion of the scale component is remarkable when the pipe wall temperature is high, the water velocity is low, and the water passage has a bend with a small radius of curvature.

[0003]

Accumulation of deposits of scale components on the tube wall as described above results in a decrease in heat transfer performance from the tube wall, resulting in a decrease in performance as a heat exchanger. The flow passage cross-sectional area of the water passage becomes small, causing a problem such as clogging of the flow passage.

The present invention has been made in view of the above points, and can suppress the adhesion of scale components to the inner wall of the core tube in a heat exchanger in which a winding tube is spirally wound around the outer circumference of the core tube. The purpose is to do so.

[0005]

According to the invention of claim 1, as a means for solving the above-mentioned problems, a core tube 1 forming a water passage W and a spiral winding around the core tube 1 are provided. The water passage W, which is composed of the winding tube 2 that constitutes the refrigerant passage R,
In the heat exchanger configured to heat the water flowing through the refrigerant by the refrigerant flowing through the refrigerant passage R, a portion A at the outlet portion of the water passage W where the water temperature is equal to or higher than a predetermined temperature.
The winding pitch P ′ of the winding tube 2 is larger than the winding pitch P on the upstream side of the portion.

With the above-mentioned structure, the outlet portion of the water passage W where the water temperature is equal to or higher than the predetermined temperature A (that is, the portion where the water temperature at which calcium carbonate, which is a scale component, precipitates) ), The winding pitch P ′ of the winding tube 2 becomes sparse, and the amount of heat transfer from the refrigerant flowing in the winding tube 2 in the portion A to the core tube 1 side becomes small. Therefore, the tube wall temperature of the core tube 1 in the portion A is lowered, the deposition of scale components is suppressed, and the scale adhesion to the tube wall of the core tube 1 is suppressed.

According to the second aspect of the invention, as a means for solving the above-mentioned problems, the core tube 1 forming the water passage W and the refrigerant passage R spirally wound around the outer periphery of the core tube 1 are formed. A heat exchanger comprising a winding tube 2 and configured to heat the water flowing in the water passage W by the refrigerant flowing in the refrigerant passage R, wherein the water temperature at the outlet of the water passage W is equal to or higher than a predetermined temperature. The winding tube 2 in the portion A that is formed is parallel to the tube axis of the core tube 1 along the core tube 1.

By virtue of the above construction, the portion A at the outlet of the water passage W where the water temperature is equal to or higher than a predetermined temperature (that is, the portion where the water temperature at which calcium carbonate, which is a scale component, precipitates) ) Is a core tube 1
The heat transfer amount from the refrigerant flowing in the winding tube 2 in the portion A to the core tube 1 side becomes small in parallel with the tube axis of the above. Therefore, the tube wall temperature of the core tube 1 in the portion A is lowered, the deposition of scale components is suppressed, and the scale adhesion to the tube wall of the core tube 1 is suppressed.

According to the third aspect of the present invention, as a means for solving the above-mentioned problems, the core tube 1 which is formed in a spiral shape and constitutes the water passage W, and the core tube 1 is spirally wound around the outer circumference thereof. In the heat exchanger, which comprises a winding tube 2 forming a refrigerant passage R, and which heats water flowing in the water passage W by the refrigerant flowing in the refrigerant passage R, the core tube 1
The center side of the spiral in the above is used as the water inlet 8, and the outer peripheral side of the spiral in the core tube 1 is used as the water outlet 9.

With the above construction, the radius of curvature of the outlet side portion of the water passage W where the pipe wall temperature rises becomes large, so that adhesion of scale components is suppressed.

In a fourth aspect of the present invention, as a means for solving the above problems, a core tube 1 which is formed in a spiral shape and constitutes a water passage W, and a core tube 1 which is spirally wound around the outer circumference of the core tube 1. In a heat exchanger that is composed of a winding tube 2 that forms a refrigerant passage R, and that heats water flowing in the water passage W by the refrigerant flowing in the refrigerant passage R, the outlet 9 of the water passage W is It is provided on the outer peripheral side of the spiral in the core tube 1.

With the above construction, the radius of curvature of the outlet side portion of the water passage W where the temperature of the pipe wall becomes high becomes large, so that the adhesion of scale components is suppressed.

As in the invention of claim 5, claim 4
In the heat exchanger described above, a plurality of the core tubes 1 formed in the spiral shape are stacked so as to form a series of water passages W, and a final outlet 9 of the water passages W is formed in the core tube 1. When it is provided on the outer peripheral side of the spiral, the performance of the heat exchanger can be significantly improved by a simple method of stacking a plurality of spiral-shaped core tubes 1 (in other words, if the same performance is exhibited). Since the volume of the heat exchanger can be minimized) and the radius of curvature of the outlet side portion of the water passage W where the pipe wall temperature becomes high becomes large, the adhesion of scale components can be suppressed.

As in the invention of claim 6, claim 5
In the heat exchanger described above, when the inlet 8 of the water passage W is provided on the outer peripheral side of the spiral in the core tube 1 and the water passage W is communicated with the center side of the spiral in the core tube 1, In the heat exchanger having a shape in which the spiral core tubes 1 are superposed, a smooth water passage W can be formed, and the inlet 8 and the outlet 9 of the water passage W can be formed at the same portion, so that water supply / discharge can be performed. The structure of the means can be simplified.

[0015] As in the invention of claim 7, in the heat exchanger according to any one of claims 3, 4, 5 and 6, the water temperature at the outlet of the water passage W becomes equal to or higher than a predetermined temperature. The winding pitch P'of the winding tube 2 in the portion A is the winding pitch P on the upstream side of the portion A.
When it is made larger, the winding of the winding tube 2 at the outlet portion A of the water passage W where the water temperature is equal to or higher than a predetermined temperature (that is, the portion where the water temperature at which calcium carbonate, which is a scale component, precipitates) is reached. Since the pitch P'is sparse, the amount of heat transferred from the refrigerant flowing in the winding tube 2 in the portion A to the core tube 1 side is reduced, and the tube wall temperature of the core tube 1 in the portion A is lowered. As a result, precipitation of scale components is suppressed, and scale adhesion to the tube wall of the core tube 1 is further suppressed.

As in the invention of claim 8, in the heat exchanger according to any one of claims 3, 4, 5 and 6, the water temperature at the outlet of the water passage W becomes equal to or higher than a predetermined temperature. When the winding tube 2 in the portion A is parallel to the tube axis of the core tube 1 along the core tube 1, the water temperature at the outlet of the water passage W is equal to or higher than a predetermined temperature. Since the winding tube 2 in the portion A (that is, the portion at which the water temperature at which calcium carbonate as the scale component is deposited) is parallel to the tube axis of the core tube 1, it flows in the winding tube 2 in the portion A. The amount of heat transferred from the refrigerant to the core tube 1 side is reduced, and the temperature of the tube wall of the core tube 1 in the portion A is lowered, so that the precipitation of scale components is suppressed and the tube wall of the core tube 1 is suppressed. That the scale adhesion to the That.

As in the invention of claim 9, claim 8
In the heat exchanger described in the above, when the winding tube 2 of the curved portion 1a of the core tube 1 in the portion A is parallel to the tube axis of the core tube 1 along the outside of the core tube 1, the core tube 1 The flow velocity of the water flowing through the curved portion 1a is high at the outer side and low at the inner side, whereas the outer side of the curved portion 1a becomes a high temperature portion due to the heat transfer from the winding tube 2 and the inner portion becomes a low temperature portion. Therefore, the outside of the curved portion 1a, which is the high flow velocity side where the scale component is less likely to adhere, is a high temperature portion where the scale component is likely to adhere (on the contrary, on the low flow velocity side where the scale component is likely to adhere, The inside of a certain curved portion 1a serves as a low temperature portion where the scale component hardly adheres), and the adhesion of the scale component on the curved portion 1a can be suppressed as a whole.

In the heat exchanger according to any one of claims 1, 2, 3, 4, 5, 6, 7, 8 and 9, as in the invention of claim 10, the outlet portion of the water passage W is provided. When the flow passage cross-sectional area of the water passage W in the portion A in which the water temperature is equal to or higher than the predetermined temperature is larger than the flow passage cross-sectional area on the upstream side of the portion A, it is the outlet portion of the water passage W. And the flow passage cross-sectional area of the water passage W in the portion A where the water temperature is equal to or higher than the predetermined temperature (that is, the portion where the water temperature at which calcium carbonate as a scale component is deposited) is
Since it is larger than the flow passage cross-sectional area on the upstream side of the portion A, even if the scale component adheres to the pipe wall in the portion A, the time until the water passage W is closed can be lengthened. On the contrary, in the upstream portion of the water passage W where the water temperature is low and the heat transfer coefficient of water is low, the flow passage cross-sectional area is reduced and the flow velocity is increased, so that the heat exchange performance can be improved. it can.

In the eleventh aspect of the present invention, as a means for solving the above-mentioned problems, the core tube 1 forming the water passage W and the refrigerant passage R formed by spirally winding the outer periphery of the core tube 1 are formed. A heat exchanger comprising a winding tube 2 and configured to heat the water flowing in the water passage W by the refrigerant flowing in the refrigerant passage R, wherein the water temperature at the outlet of the water passage W is equal to or higher than a predetermined temperature. The flow passage cross-sectional area of the water passage W in the portion A is larger than the flow passage cross-sectional area on the upstream side of the portion A.

By virtue of the above construction, the outlet portion of the water passage W where the water temperature is equal to or higher than a predetermined temperature (that is, the portion where the water temperature at which calcium carbonate, which is a scale component, precipitates) ), The flow passage cross-sectional area of the water passage W is larger than the flow passage cross-sectional area on the upstream side of the portion A. Therefore, even if the scale component adheres to the pipe wall of the portion A, the water passage W is You can lengthen the time until it is blocked. On the contrary, in the upstream portion of the water passage W where the water temperature is low and the heat transfer coefficient of water is low, the flow passage cross-sectional area is reduced and the flow velocity is increased, so that the heat exchange performance can be improved. it can.

According to the twelfth aspect of the present invention, as means for solving the above-mentioned problems, a plurality of core tubes 1, 1 ... Having a predetermined length arranged in parallel and spirals on the outer circumference of each core tube 1 are provided. , And the core tubes 1, 1 ... Connected via the U-shaped passages 5, 5 ... of the manifold 6 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, and the water flowing in the water passage W is heated by the refrigerant flowing in the refrigerant passage R. In the heat exchanger configured as described above, the inner volume of each U-shaped passage 5 is increased so as to function as a scale adhering tank.

With the above construction, the portion of the manifold 6 having a large internal volume in the U-shaped passage 5 functions as a scale adhering tank, and the scale component is deposited in the U-shaped passage 5. The concentration of the scale component on the downstream side of the U-shaped passage 5 is lowered, and as a result, the adhesion of the scale component to the pipe wall is suppressed.

As in the thirteenth aspect of the present invention, in the heat exchanger according to the twelfth aspect, the manifold 6 is provided with scale adhesion promoting means 14 for promoting scale adhesion to the U-shaped passages 5. The adhesion of the scale component to the U-shaped passage 5 in the manifold 6 is actively promoted, and the concentration of the scale component on the downstream side of the U-shaped passage 5 is further reduced, and as a result, the core tube The adhesion of the scale component to the tube wall of No. 1 is further suppressed.

As in the invention of claim 14, in the heat exchanger according to claim 13, when the scale adhesion promoting means 14 is a high temperature refrigerant before being supplied to the refrigerant passage R, a high temperature refrigerant is retained. Manifold 6 due to heat
By heating the U-shaped passage 5, the scale adhesion is promoted, and it is not necessary to provide any special means.

As in the invention of claim 15, in the heat exchanger according to any one of claims 12, 13 and 14, when the manifold 6 is replaceable, the U-shaped passage 5 in the manifold 6 is By replacing the scale component before it is blocked due to adhesion, troubles such as equipment stoppage can be prevented.

As in the sixteenth aspect of the present invention, in the heat exchanger according to any one of the twelfth, thirteenth, fourteenth and fifteenth aspects, the water temperature at the outlet portion of the water passage W becomes equal to or higher than a predetermined temperature. When the winding pitch P ′ of the winding tube 2 in the portion A is larger than the winding pitch P on the upstream side of the portion A, the outlet portion of the water passage W and the water temperature is equal to or higher than a predetermined temperature. Since the winding pitch P ′ of the winding tube 2 in A (that is, the portion at which the water temperature at which calcium carbonate, which is a scale component is deposited), is sparse, the core from the refrigerant flowing in the winding tube 2 in the portion A is wicked. The amount of heat transfer to the tube 1 side becomes small, and the part A
Therefore, the temperature of the tube wall of the core tube 1 is reduced, so that the precipitation of scale components is suppressed, and the adhesion of scale to the tube wall of the core tube 1 is further suppressed.

As in the invention of claim 17, 12,
In the heat exchanger according to any one of 13, 14, and 15, the winding tube 2 in a portion A where the water temperature is equal to or higher than a predetermined temperature, which is an outlet portion of the water passage W, is In the case of being parallel to the pipe axis, winding at the outlet portion of the water passage W where the water temperature is equal to or higher than a predetermined temperature (that is, the portion where the water temperature at which calcium carbonate, which is a scale component, precipitates) Since the tube 2 is parallel to the tube axis of the core tube 1, the amount of heat transfer from the refrigerant flowing in the winding tube 2 in the portion A to the core tube 1 side is small, and the tube of the core tube 1 in the portion A is small. Since the wall temperature is lowered, the deposition of scale components is suppressed, and the scale adhesion to the tube wall of the core tube 1 is further suppressed.

As in the eighteenth aspect of the present invention, in the heat exchanger according to any one of the twelfth, thirteenth, fourteenth, fifteenth, sixteenth and seventeenth aspects, the water temperature is predetermined at the outlet portion of the water passage W. When the flow passage cross-sectional area of the water passage W in the portion A having a temperature equal to or higher than the temperature is made larger than the flow passage cross-sectional area on the upstream side of the portion A, the water temperature at the outlet portion of the water passage W is equal to or higher than a predetermined temperature. The flow passage cross-sectional area of the water passage W in the portion A (that is, the portion at which the water temperature at which calcium carbonate as a scale component is deposited) is
Since it is larger than the flow passage cross-sectional area on the upstream side of the portion A, even if the scale component adheres to the pipe wall in the portion A, the time until the water passage W is closed can be lengthened. On the contrary, in the upstream portion of the water passage W where the water temperature is low and the heat transfer coefficient of water is low, the flow passage cross-sectional area is reduced and the flow velocity is increased, so that the heat exchange performance can be improved. it can.

[0029]

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 heat exchanger for water used as a heater in a heat pump water heater, and as shown in FIG. 1, has a predetermined length arranged in parallel on the same plane. , A plurality of core tubes 1, and each core tube 1
The winding tubes 2, 2 that are spirally wound around the outer circumference of
・ 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 portion to form a series of water passages W, while the winding pipes 2, 2 ... Are connected to the winding pipe connecting portion. (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). Reference numeral 8 is an inlet of the water passage W, 9 is an outlet of the water passage W,
Reference numeral 10 is an inlet of the refrigerant passage R, and 11 is an outlet of the refrigerant passage R.

A portion A (in the case of the present embodiment, the outlet side of the water passage W) where the water temperature is equal to or higher than a predetermined temperature (a temperature at which calcium carbonate as a scale component is deposited, for example, 70 ° C.) The winding pitch P ′ of the winding tube 2 in the last one core tube 1) is larger than the winding pitch P on the upstream side of the portion A.

In the case of the above construction, the portion A at the outlet of the water passage W where the water temperature is equal to or higher than the predetermined temperature.
Since the winding pitch P'of the winding tube 2 in the portion (that is, the portion at which the water temperature at which calcium carbonate, which is a scale component is deposited), is sparse, the core pipe from the refrigerant flowing inside the winding tube 2 in the portion A is sparse. The amount of heat transfer to the No. 1 side is reduced, the temperature of the tube wall of the core tube 1 in the portion A is lowered, and the precipitation of scale components is suppressed, so that the scale adheres to the tube wall of the core tube 1. Will be suppressed.

In this embodiment, the winding pitch P'in the portion A is the same, but the winding pitch in the portion A may be increased toward the outlet side. Further, the part A may be set so as to include the last second core tube 1 on the outlet side.

Second Embodiment FIG. 2 shows a heat exchanger according to a second embodiment of the present invention.

This heat exchanger also constitutes a water heat exchanger used as a heater in a heat pump water heater, and as shown in FIG. 2, it is swirled to form an elliptical shape on the same plane. A core tube 1 serving as a water passage W formed in a shape and a winding tube 2 serving as a refrigerant passage R that is spirally wound around the outer circumference of the core tube 1.

The center side of the spiral in the core tube 1 serves as a water inlet 8, and the outer peripheral side of the spiral in the core tube 1 serves as a water outlet 9. Reference numeral 10 is a refrigerant passage R
And 11 is an outlet of the refrigerant passage R.

Further, the winding tube 2 at the outlet portion A of the water passage W where the water temperature is equal to or higher than a predetermined temperature (for example, the portion where the water temperature at which calcium carbonate, which is a scale component, precipitates) is reached. Is larger than the winding pitch P on the upstream side of the portion A.

In the case of the above construction, the portion A at the outlet of the water passage W where the water temperature is equal to or higher than a predetermined temperature.
Since the winding pitch P'of the winding tube 2 in the portion (that is, the portion at which the water temperature at which calcium carbonate, which is a scale component is deposited), is sparse, the core pipe from the refrigerant flowing inside the winding tube 2 in the portion A is sparse. The amount of heat transfer to the No. 1 side is reduced, the temperature of the tube wall of the core tube 1 in the portion A is lowered, and the precipitation of scale components is suppressed, so that the scale adheres to the tube wall of the core tube 1. Will be suppressed.

In the present embodiment, the winding pitch P'in the portion A is the same, but the winding pitch in the portion A may be increased toward the outlet side.

Further, since the center side of the spiral in the core tube 1 is used as the water inlet 8 and the outer peripheral side of the spiral in the core tube 1 is used as the water outlet 9, the outlet of the water passage W where the pipe wall temperature becomes high. Since the radius of curvature of the side portion becomes large, the adhesion of the scale component is suppressed also at this point.

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.).

Third Embodiment FIG. 3 shows a heat exchanger according to a third embodiment of the present invention.

In this case, in the heat exchanger according to the first embodiment (the heat exchanger shown in FIG. 1), the portion A at the outlet of the water passage W where the water temperature is equal to or higher than a predetermined temperature.
(In the case of this embodiment, the last one core tube 1 on the outlet side)
Without winding the winding tube 2 in
It is parallel to the tube axis of the core tube 1 along the core tube 1.

By virtue of the above-mentioned structure, the outlet portion of the water passage W, where the water temperature is equal to or higher than the predetermined temperature A (that is, the portion where the water temperature at which calcium carbonate, which is a scale component, precipitates) ) Is a core tube 1
The heat transfer amount from the refrigerant flowing in the winding tube 2 in the portion A to the core tube 1 side becomes small in parallel with the tube axis of the above. Therefore, the tube wall temperature of the core tube 1 in the portion A is lowered, the deposition of scale components is suppressed, and the scale adhesion to the tube wall of the core tube 1 is suppressed. The above part A is the last two on the exit side.
You may set so that the core tube 1 of the real may be included.

The rest of the configuration, functions and effects are the same as in the first embodiment, so a description thereof will be omitted.

Fourth Embodiment FIGS. 4 and 5 show the essential parts of a heat exchanger according to a fourth embodiment of the present invention.

In this case, in the heat exchanger according to the second embodiment (the heat exchanger shown in FIG. 2), the portion in the portion A at the outlet of the water passage W where the water temperature is equal to or higher than a predetermined temperature. The winding tube 2 is parallel to the tube axis of the core tube 1 along the core tube 1 without being spirally wound.
In this case, since the curved portion 1a of the spiral core tube 1 is included in the portion A, in the curved portion 1a, as shown in FIG. 4 and FIG.
It is parallel to the tube axis of the core tube 1 along the outside of the core tube 1.

With the above construction, the winding tube 2 in the portion A at the outlet of the water passage W where the water temperature is equal to or higher than a predetermined temperature is provided along the core tube 1 with the core tube 1. When it is parallel to the pipe axis of No. 1, a portion A where the water temperature is equal to or higher than a predetermined temperature at the outlet portion of the water passage W (that is, a portion where the water temperature at which calcium carbonate, which is a scale component, precipitates) Since the winding tube 2 in is parallel to the tube axis of the core tube 1, the amount of heat transferred from the refrigerant flowing in the winding tube 2 in the portion A to the core tube 1 side is small, and the core tube 1 in the portion A is As a result, the temperature of the tube wall is reduced, so that the precipitation of scale components is suppressed, and the scale adhesion to the tube wall of the core tube 1 is further suppressed.

In addition, in this case, in the curved portion 1a of the core tube 1, the flow velocity of the water flowing through the curved portion 1a of the core tube 1 becomes high at the outside and low at the inside, whereas Since 2 is parallel to the tube axis of the core tube 1 along the outside of the core tube 1, the outside of the curved portion 1a becomes a high temperature portion due to heat transfer from the winding tube 2, and the inside is a low temperature portion. Has become. Therefore, the outside of the curved portion 1a on the high flow velocity side where the scale component is unlikely to adhere is a high temperature portion where the scale component is likely to adhere, and conversely, the curved portion 1a on the low flow velocity side where the scale component is likely to adhere. The inside of the area becomes a low-temperature portion where the scale component does not easily adhere, and as a whole, the scale component can be suppressed from adhering to the curved portion 1a.

In the present embodiment, the winding tube 2 in the entire area of the portion A is parallel to the tube axis of the core tube 1 along the outside of the core tube 1, but the core tube bending portion The winding tube 2 may be located outside only in 1a.

The other structure, functions and effects are the same as those in the second embodiment, and the explanation thereof is omitted.

Fifth Embodiment FIG. 6 shows a heat exchanger according to a fifth embodiment of the present invention.

In this case, in the heat exchanger according to the second embodiment (heat exchanger shown in FIG. 2), the portion A at the outlet of the water passage W where the water temperature is equal to or higher than a predetermined temperature.
The flow path cross-sectional area of the water passage W in the portion (that is, the water temperature at which the scale component calcium carbonate is deposited) is larger than the flow path cross-sectional area on the upstream side of the portion A. In this case, the diameter of the core tube 1'in the portion A is increased. Reference numeral 12 is a connecting pipe. In this case, the winding pitch P'of the winding tube 2 in the portion A is the same as the winding pitch P of the winding tube 2 on the upstream side of the portion A.

By virtue of the above-mentioned structure, the portion A at the outlet of the water passage W where the water temperature is equal to or higher than a predetermined temperature (that is, the portion where the water temperature at which calcium carbonate, which is a scale component, precipitates) ), The flow passage cross-sectional area of the water passage W is larger than the flow passage cross-sectional area on the upstream side of the portion A. Therefore, even if the scale component adheres to the pipe wall of the portion A, the water passage W is You can lengthen the time until it is blocked. On the contrary, in the upstream portion of the water passage W where the water temperature is low and the heat transfer coefficient of water is low, the flow passage cross-sectional area is reduced and the flow velocity is increased, so that the heat exchange performance can be improved. it can.

In the heat exchanger according to this embodiment, as in the second embodiment, a portion A (for example, an outlet portion of the water passage W where the water temperature is equal to or higher than a predetermined temperature) (for example, The winding pitch P ′ of the winding tube 2 in a portion where the water temperature at which calcium carbonate, which is a scale component is deposited, is set to be larger than the winding pitch P on the upstream side of the portion. In this case, the time from when the scale component is prevented from adhering to the portion A to when the water passage W is closed can be made longer.

The rest of the configuration, functions and effects are the same as in the second embodiment, so a description thereof will be omitted.

Sixth Embodiment FIG. 7 shows a heat exchanger according to a sixth embodiment of the present invention.

In this case, in the heat exchanger according to the second embodiment (heat exchanger shown in FIG. 2), the portion A at the outlet of the water passage W where the water temperature is equal to or higher than the predetermined temperature.
The flow path cross-sectional area of the water passage W in the portion (that is, the water temperature at which the scale component calcium carbonate is deposited) is larger than the flow path cross-sectional area on the upstream side of the portion A. In this case, in the part A, 2
The two core tubes 1 ′, 1 ′ are used, and by connecting the two core tubes 1 ′, 1 ′ to the core tube 1 on the upstream side of the portion A via the bifurcated joint 13, The cross-sectional area of the flow channel is increased. In this case, the winding tube 2 in the part A is shared by the two core tubes 1 ', 1',
The winding pitch P ′ is the same as the winding pitch P of the winding tube 2 on the upstream side of the portion A.

By virtue of the above-described structure, the outlet portion of the water passage W, where the water temperature is equal to or higher than the predetermined temperature A (that is, the portion where the water temperature at which the scale component calcium carbonate is deposited is reached) ), The flow passage cross-sectional area of the water passage W is larger than the flow passage cross-sectional area on the upstream side of the portion A. Therefore, even if the scale component adheres to the pipe wall of the portion A, the water passage W is You can lengthen the time until it is blocked. On the contrary, in the upstream portion of the water passage W where the water temperature is low and the heat transfer coefficient of water is low, the flow passage cross-sectional area is reduced and the flow velocity is increased, so that the heat exchange performance can be improved. it can.

In the heat exchanger according to this embodiment, one winding tube 2 is commonly wound around two core tubes 1 ', 1', but two core tubes are used. In some cases, the winding tube 2 may be individually wound around 1'and 1 '.

As in the second embodiment, the portion A at the outlet of the water passage W where the water temperature is equal to or higher than a predetermined temperature (for example, the water temperature at which calcium carbonate, which is a scale component, precipitates) The winding pitch P ′ of the winding tube 2 in the portion (in which the portion is formed) can be made larger than the winding pitch P on the upstream side of the portion. in this case,
It is possible to further lengthen the time from when the adhesion of the scale component in the portion A is suppressed to when the water passage W is closed.

The rest of the configuration, functions and effects are the same as in the second embodiment, so a description thereof will be omitted.

Seventh Embodiment FIG. 8 shows a heat exchanger according to a seventh embodiment of the present invention.

In this case, in the heat exchanger according to the first embodiment (heat exchanger shown in FIG. 1), the water temperature at the outlet of the water passage W is at a predetermined temperature (ie, calcium carbonate which is a scale component). Is equal to or higher than the water temperature at which water is deposited) (in the case of the present embodiment, the flow passage cross-sectional area of the water passage W in the last one core tube 1'on the outlet side) is equal to
It is made larger than the flow path cross-sectional area on the upstream side.
In this case, the diameter of the core tube 1'constituting the portion A is increased. It should be noted that, as in the sixth embodiment, 2
The channel cross-sectional area may be increased by using the core tubes 1 ', 1'.

Further, in the case of the present embodiment, the portion A (the present embodiment) where the water temperature is equal to or higher than the predetermined temperature (that is, the water temperature at which calcium carbonate, which is a scale component, is deposited) at the outlet of the water passage W In the case of the configuration, the winding pitch P ′ of the winding tube 2 in the last one core tube 1) on the outlet side is made larger than the winding pitch P on the upstream side of the relevant portion.

By virtue of the above construction, the portion A at the outlet of the water passage W where the water temperature is equal to or higher than the predetermined temperature (that is, the portion where the water temperature at which the scale component calcium carbonate precipitates) ), The flow passage cross-sectional area of the water passage W is larger than the flow passage cross-sectional area on the upstream side of the portion A. Therefore, even if the scale component adheres to the pipe wall of the portion A, the water passage W is You can lengthen the time until it is blocked. On the contrary, in the upstream portion of the water passage W where the water temperature is low and the heat transfer coefficient of water is low, the flow passage cross-sectional area is reduced and the flow velocity is increased, so that the heat exchange performance can be improved. it can.

In the heat exchanger according to the present embodiment, the outlet A of the water passage W where the water temperature is equal to or higher than the predetermined temperature (that is, the water temperature at which the scale component calcium carbonate is deposited) Since the winding pitch P ′ of the winding tube 2 in the portion (2) is larger than the winding pitch P on the upstream side of the portion, the adhesion of scale components in the portion A is suppressed. The time until the water passage W is closed can be extended. The winding pitch of the winding tube 2 may be the same throughout the water passage W.

The rest of the configuration, functions, and effects are the same as those in the first embodiment, so a description thereof will be omitted.

Eighth Embodiment FIG. 9 shows a heat exchanger according to an eighth embodiment of the present invention.

This heat exchanger comprises a plurality of core tubes 1, 1 ... Which are arranged in parallel and have a predetermined length, and winding tubes 2, 2 ... which are spirally wound around the outer circumference of each core tube 1. ., And the core tubes 1, 1 ... Are connected via the U-shaped passages 5, 5 ... of the manifold 6 to form a series of water passages W, and the winding tubes 2, 2 ... Are connected to each other through the winding tube connecting portion 7 to form a series of refrigerant passages R.
The water flowing through the water passage W is heated by the refrigerant flowing through the refrigerant passage R. The manifold 6 is replaceable.

In this heat exchanger, the inner volume of each U-shaped passage 5 is increased so that the U-shaped passage 5 functions as a scale adhering tank.

With the above structure, the portion of the manifold 6 having a large internal volume in the U-shaped passage 5 functions as a scale adhering tank, and the scale component is deposited in the U-shaped passage 5. The concentration of the scale component on the downstream side of the U-shaped passage 5 is lowered, and as a result, the adhesion of the scale component to the tube wall of the core tube 1 is suppressed. Also, since the manifold 6 is replaceable, the U-shaped passage 5 in the manifold 6
By replacing the product before it is blocked due to the adhesion of scale components, troubles such as equipment stoppage can be prevented.

By the way, also in the present embodiment, the winding pitch P'of the winding tube 2 in the portion A at the outlet of the water passage W where the water temperature is equal to or higher than the predetermined temperature is set on the upstream side of the portion A. It may be made larger than the winding pitch P to lower the temperature of the tube wall of the core tube 1 in the portion A so as to suppress the scale from adhering to the tube wall. The winding tube 2 in the portion A where the temperature is equal to or higher than the predetermined temperature (that is, the portion where the water temperature at which the scale component calcium carbonate is deposited) is the core tube 1.
May be parallel to the tube axis of the core tube 1 to reduce the temperature of the tube wall of the core tube 1 in the portion A to suppress the scale adhesion to the tube wall. The flow passage cross-sectional area of the water passage W in the portion A where the water temperature is equal to or higher than a predetermined temperature is made larger than the flow passage cross-sectional area on the upstream side of the portion A, and the scale component adheres to the pipe wall. The water passage W in the portion A may not be closed.

Ninth Embodiment FIG. 10 shows a heat exchanger according to the ninth embodiment of the present invention.

In this case, in the heat exchanger according to the eighth embodiment (heat exchanger shown in FIG. 9), the manifold 6 has a scale adhesion promoting means for promoting scale adhesion to each U-shaped passage 5. 14 is attached. In the present embodiment, the refrigerant pipe 16 connected to the inlet 10 of the refrigerant passage R via the flow divider 15 is passed through in the vicinity of the U-shaped passages 5, 5, ... Inside the manifolds 6, 6. Is configured. That is, the scale adhesion promoting means 1
A high-temperature refrigerant flowing through the refrigerant pipe 16 is adopted as No. 4. This way, the manifold 6
The adhesion of the scale component to the U-shaped passage 5 is positively promoted by the scale adhesion promoting means 14, and the concentration of the scale component on the downstream side of the U-shaped passage 5 is further lowered, and as a result, Therefore, the adhesion of scale components to the tube wall of the core tube 1 is further suppressed.
In addition, the heat of the high-temperature refrigerant flowing through the refrigerant pipe 16 heats the U-shaped passage 5 of the manifold 6 to accelerate the scale adhesion, and it is not necessary to provide any special means.

As the scale adhesion promoting means 14, any heating means such as an electric heater may be used as long as it can heat the U-shaped passage 5.

The other structure, function and effect are the same as those in the eighth embodiment, and therefore the explanation thereof is omitted.

The embodiments described above (that is, the first to ninth embodiments) are disclosed in the above specification and drawings.

The newly added embodiment (that is, the tenth embodiment) will be described below.

Tenth Embodiment FIGS. 11 to 13 show a heat exchanger according to a tenth embodiment of the present invention.

In this case, a series of water passages W is formed by connecting the spirally shaped core tubes 1 in an upper and lower two stages (that is, two pipes) in an overlapping manner. The upper core tube 1 and the lower core tube 1 are connected to each other via a connecting portion 17 on the center side of the spiral, and are wound around the upper core tube 1 and the lower core tube 1. It is connected to the wound tube 2 via the connecting portion 18 on the center side of the spiral. The inlet 8 of the water passage W is provided on the outer peripheral side of the spiral in the lower core tube 1, and the final outlet 9 of the water passage is provided on the outer peripheral side of the spiral in the upper core tube 1. Further, the outlet portion of the water passage W (that is, the outlet portion of the upper core tube 1) where the water temperature is equal to or higher than a predetermined temperature (that is, the water temperature at which the scale component calcium carbonate is deposited). The flow passage cross-sectional area of the water passage W in the portion) is larger than the flow passage cross-sectional area on the upstream side of the portion A. In this case, the part A
In the above, a core tube 1'having a larger diameter than the core tube 1 on the upstream side of the portion A is used. Reference numeral 12 is a connecting pipe.
In this case, the winding pitch of the winding tube 2 in the part A,
The winding pitch of the winding tube 2 on the upstream side of the portion A is the same.

With the above-mentioned structure, the performance of the heat exchanger can be greatly improved by a simple method of stacking the spiral core tubes 1 in two stages (in other words, in other words).
If the same performance is exhibited, the volume of the heat exchanger can be minimized) and the radius of curvature of the outlet side portion of the water passage W where the temperature of the pipe wall becomes high becomes large. Can be suppressed.

Further, in the heat exchanger having a shape in which the spiral core tubes 1 are superposed, a smooth water passage W can be formed, and the inlet 8 and the outlet 9 of the water passage W can be formed at the same portion. The structure of water supply / discharge means can be simplified.

Further, the flow of the water passage W at the outlet A of the water passage W where the water temperature is equal to or higher than a predetermined temperature (that is, the portion where the water temperature is such that calcium carbonate, which is a scale component, is deposited). Since the road cross-sectional area is larger than the flow path cross-sectional area on the upstream side of the portion A,
Even if the scale component adheres to the pipe wall in the portion A, the time until the water passage W is closed can be increased, and conversely, the water temperature is low and the heat transfer coefficient of water is low. In the upstream portion of the water passage W, the flow passage cross-sectional area is reduced and the flow velocity is increased, so that the heat exchange performance can be improved.

As in the second embodiment, a portion A at the outlet of the water passage W where the water temperature is equal to or higher than a predetermined temperature (for example, the water temperature at which calcium carbonate, which is a scale component, precipitates) It is also possible to make the winding pitch of the winding tube 2 in the portion) larger than the winding pitch in the upstream side of the portion. In this case, the time from when the scale component is prevented from adhering to the portion A to when the water passage W is closed can be made longer. Further, as in the fourth embodiment shown in FIGS. 4 and 5, the winding tube 2 in the portion A at the outlet of the water passage W where the water temperature is equal to or higher than a predetermined temperature is formed into a spiral shape. It may be parallel to the tube axis of the core tube 1 along the core tube 1 without being wound. In this case, the curved portion 1a of the spiral core tube 1
Is included in the portion A, the curved portion 1a is
In the above, the winding tube 2 is preferably parallel to the tube axis of the core tube 1 along the outside of the core tube 1.

In the present embodiment, the core tubes 1 are stacked in two stages, but the core tubes 1 may be stacked in three or more stages. In that case, a heat exchanger having higher performance can be obtained. You can

[0088]

According to the invention of claim 1, the core tube 1 forming the water passage W and the winding tube 2 forming the refrigerant passage R by being spirally wound around the outer periphery of the core tube 1. In the heat exchanger configured to heat the water flowing through the water passage W by the refrigerant flowing through the refrigerant passage R, the water passage W
The winding pitch P'of the winding tube 2 in the portion A, which is the exit portion of the water temperature above the predetermined temperature, is made larger than the winding pitch P on the upstream side of the portion, and the winding tube 2 in the portion A is Since the amount of heat transferred from the refrigerant flowing inside to the core tube 1 side is reduced, the temperature of the wall of the core tube 1 in the portion A is lowered,
The deposition of the scale component is suppressed, and the scale adhesion to the tube wall of the core tube 1 is suppressed.

According to the second aspect of the invention, the core tube 1 forming the water passage W and the winding tube 2 spirally wound around the core tube 1 to form the refrigerant passage R are formed. In the heat exchanger configured to heat the water flowing in the water passage W by the refrigerant flowing in the refrigerant passage R, the winding in the portion A at the outlet portion of the water passage W in which the water temperature is equal to or higher than a predetermined temperature. The tube 2 along with the core tube 1
Since the amount of heat transfer from the refrigerant flowing in the winding tube 2 in the portion A to the core tube 1 side is made small in parallel with the tube axis of, the temperature of the wall of the core tube 1 in the portion A decreases. As a result, precipitation of scale components is suppressed, and scale adhesion to the tube wall of the core tube 1 is suppressed.

According to the third aspect of the present invention, the core tube 1 which is formed in a spiral shape and forms the water passage W, and the winding tube which is spirally wound around the outer periphery of the core tube 1 to form the refrigerant passage R Two
And the water flowing through the water passage W through the refrigerant passage R
In the heat exchanger configured to be heated by the refrigerant flowing in the core, the center side of the spiral in the core tube 1 is connected to the water inlet 8
In addition, since the outer peripheral side of the spiral in the core tube 1 is used as the water outlet 9, the radius of curvature of the outlet side portion of the water passage W where the tube wall temperature increases becomes large, and adhesion of scale components is suppressed. The effect is that

According to the invention of claim 4, the core tube 1 which is formed in a spiral shape to form the water passage W, and the winding tube which is spirally wound around the outer periphery of the core tube 1 to form the refrigerant passage R Two
And the water flowing through the water passage W through the refrigerant passage R
In the heat exchanger configured to be heated by the refrigerant flowing through the water passage W, the outlet 9 of the water passage W is provided on the outer peripheral side of the spiral in the core tube 1 to increase the pipe wall temperature.
Since the radius of curvature of the outlet side of is increased,
There is an effect that it is possible to suppress the adhesion of the scale component in the portion.

As in the invention of claim 5, claim 4
In the heat exchanger described above, the core tubes 1 formed in the spiral shape are stacked in a plurality of stages so as to form one continuous water passage W, and the final outlet 9 of the water passage W is formed in the core tube 1. When it is provided on the outer peripheral side of the spiral, the performance of the heat exchanger can be significantly improved by a simple method of stacking a plurality of spiral-shaped core tubes 1 (in other words, if the same performance is exhibited). Since the volume of the heat exchanger can be minimized) and the radius of curvature of the outlet side portion of the water passage W where the pipe wall temperature becomes high becomes large, the adhesion of scale components can be suppressed.

As in the invention of claim 6, claim 5
In the heat exchanger described above, when the inlet 8 of the water passage W is provided on the outer peripheral side of the spiral in the core tube 1 and the water passage W is communicated with the center side of the spiral in the core tube 1, In the heat exchanger having a shape in which the spiral core tubes 1 are superposed, a smooth water passage W can be formed, and the inlet 8 and the outlet 9 of the water passage W can be formed at the same portion, so that water supply / discharge can be performed. The structure of the means can be simplified.

As in the invention of claim 7, in the heat exchanger according to any one of claims 3, 4, 5 and 6, the water temperature at the outlet of the water passage W becomes equal to or higher than a predetermined temperature. The winding pitch P'of the winding tube 2 in the portion A is the winding pitch P on the upstream side of the portion A.
When it is made larger, the winding of the winding tube 2 at the outlet portion A of the water passage W where the water temperature is equal to or higher than a predetermined temperature (that is, the portion where the water temperature at which calcium carbonate, which is a scale component, precipitates) is reached. Since the pitch P'is sparse, the amount of heat transferred from the refrigerant flowing in the winding tube 2 in the portion A to the core tube 1 side is reduced, and the tube wall temperature of the core tube 1 in the portion A is lowered. As a result, precipitation of scale components is suppressed, and scale adhesion to the tube wall of the core tube 1 is further suppressed.

As in the eighth aspect of the invention, in the heat exchanger according to any one of the third, fourth, fifth and sixth aspects, the water temperature at the outlet portion of the water passage W becomes equal to or higher than a predetermined temperature. When the winding tube 2 in the portion A is parallel to the tube axis of the core tube 1 along the core tube 1, the water temperature at the outlet of the water passage W is equal to or higher than a predetermined temperature. Since the winding tube 2 in the portion A (that is, the portion at which the water temperature at which calcium carbonate as the scale component is deposited) is parallel to the tube axis of the core tube 1, it flows in the winding tube 2 in the portion A. The amount of heat transferred from the refrigerant to the core tube 1 side is reduced, and the temperature of the tube wall of the core tube 1 in the portion A is reduced, so that the precipitation of scale components is suppressed and the tube wall of the core tube 1 is suppressed. That the scale adhesion to the That.

As in the invention of claim 9, claim 8
In the heat exchanger described in the above, when the winding tube 2 of the curved portion 1a of the core tube 1 in the portion A is parallel to the tube axis of the core tube 1 along the outside of the core tube 1, the core tube 1 The flow velocity of the water flowing through the curved portion 1a is high at the outer side and low at the inner side, whereas the outer side of the curved portion 1a becomes a high temperature portion due to the heat transfer from the winding tube 2 and the inner portion becomes a low temperature portion. Therefore, the outside of the curved portion 1a, which is the high flow velocity side where the scale component is less likely to adhere, is a high temperature portion where the scale component is likely to adhere (on the contrary, on the low flow velocity side where the scale component is likely to adhere, The inside of a certain curved portion 1a serves as a low temperature portion where the scale component hardly adheres), and the adhesion of the scale component on the curved portion 1a can be suppressed as a whole.

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, the outlet portion of the water passage W. When the flow passage cross-sectional area of the water passage W in the portion A in which the water temperature is equal to or higher than the predetermined temperature is larger than the flow passage cross-sectional area on the upstream side of the portion A, it is the outlet portion of the water passage W. And the flow passage cross-sectional area of the water passage W in the portion A where the water temperature is equal to or higher than the predetermined temperature (that is, the portion where the water temperature at which calcium carbonate as a scale component is deposited) is
Since it is larger than the flow passage cross-sectional area on the upstream side of the portion A, even if the scale component adheres to the pipe wall in the portion A, the time until the water passage W is closed can be lengthened. On the contrary, in the upstream portion of the water passage W where the water temperature is low and the heat transfer coefficient of water is low, the flow passage cross-sectional area is reduced and the flow velocity is increased, so that the heat exchange performance can be improved. it can.

According to the eleventh aspect of the present invention, the core tube 1 forming the water passage W and the winding tube 2 spirally wound around the core tube 1 to form the refrigerant passage R are provided. In the heat exchanger configured to heat the water flowing in the water passage W by the refrigerant flowing in the refrigerant passage R, the water passage W
Since the flow passage cross-sectional area of the water passage W in the portion A where the water temperature is equal to or higher than the predetermined temperature is larger than the flow passage cross-sectional area on the upstream side of the portion A,
Even if the scale component adheres to the pipe wall in the portion A, it is possible to increase the time until the water passage W is closed. On the contrary, the water temperature is low,
In the upstream portion of the water passage W where the heat transfer coefficient of water is low, the flow passage cross-sectional area is reduced and the flow velocity is increased, so that the heat exchange performance can be improved.

According to the twelfth aspect of the present invention, a plurality of core tubes 1, 1 ... Having a predetermined length arranged in parallel and a winding tube 2 spirally wound around the outer circumference of each core tube 1 are provided. , 2 ...
, And the core tubes 1, 1, ... Are connected through the U-shaped passages 5, 5 ... of the manifold 6 to form a series of water passages W, and the winding tubes 2, 2 ,. In the heat exchanger configured to be connected through the winding tube connection portion 7 to form a series of refrigerant passages R and to heat the water flowing in the water passage W by the refrigerant flowing in the refrigerant passage R, Since the inner volume of the U-shaped passage 5 is increased so that the U-shaped passage 5 functions as a scale adhering tank, the scale component is deposited in the U-shaped passage 5, so that the scale component on the downstream side of the U-shaped passage 5 is deposited. There is an effect that the concentration of is reduced, and as a result, the adhesion of scale components to the tube wall of the core tube 1 is suppressed.

As in the thirteenth aspect of the present invention, in the heat exchanger according to the twelfth aspect, the manifold 6 is provided with scale adhesion promoting means 14 for promoting scale adhesion to the U-shaped passages 5. The adhesion of the scale component to the U-shaped passage 5 in the manifold 6 is actively promoted, and the concentration of the scale component on the downstream side of the U-shaped passage 5 is further reduced, and as a result, the core tube The adhesion of the scale component to the tube wall of No. 1 is further suppressed.

As in the fourteenth aspect of the present invention, in the heat exchanger of the thirteenth aspect, when the scale adhesion promoting means 14 is a high temperature refrigerant before being supplied to the refrigerant passage R, a high temperature refrigerant is retained. Manifold 6 due to heat
By heating the U-shaped passage 5, the scale adhesion is promoted, and it is not necessary to provide any special means.

As in the fifteenth aspect of the invention, in the heat exchanger according to any one of the twelfth, thirteenth and fourteenth aspects, when the manifold 6 is replaceable, the U-shaped passage 5 in the manifold 6 is By replacing the scale component before it is blocked due to adhesion, troubles such as equipment stoppage can be prevented.

As in the sixteenth aspect of the present invention, in the heat exchanger according to any one of the twelfth, thirteenth, fourteenth and fifteenth aspects, the water temperature at the outlet of the water passage W becomes equal to or higher than a predetermined temperature. When the winding pitch P ′ of the winding tube 2 in the portion A is larger than the winding pitch P on the upstream side of the portion A, the outlet portion of the water passage W and the water temperature is equal to or higher than a predetermined temperature. Since the winding pitch P ′ of the winding tube 2 in A (that is, the portion at which the water temperature at which calcium carbonate, which is a scale component is deposited), is sparse, the core from the refrigerant flowing in the winding tube 2 in the portion A is wicked. The amount of heat transfer to the tube 1 side becomes small, and the part A
Therefore, the temperature of the tube wall of the core tube 1 is reduced, so that the precipitation of scale components is suppressed, and the adhesion of scale to the tube wall of the core tube 1 is further suppressed.

As in the invention of claim 17, 12,
In the heat exchanger according to any one of 13, 14, and 15, the winding tube 2 in a portion A where the water temperature is equal to or higher than a predetermined temperature, which is an outlet portion of the water passage W, is In the case of being parallel to the pipe axis, winding at the outlet portion of the water passage W where the water temperature is equal to or higher than a predetermined temperature (that is, the portion where the water temperature at which calcium carbonate, which is a scale component, precipitates) Since the tube 2 is parallel to the tube axis of the core tube 1, the amount of heat transfer from the refrigerant flowing in the winding tube 2 in the portion A to the core tube 1 side is small, and the tube of the core tube 1 in the portion A is small. Since the wall temperature is lowered, the deposition of scale components is suppressed, and the scale adhesion to the tube wall of the core tube 1 is further suppressed.

According to the eighteenth aspect of the present invention, in the heat exchanger according to any one of the twelfth, thirteenth, fourteenth, fifteenth, sixteenth and seventeenth aspects, the water temperature is predetermined at the outlet portion of the water passage W. When the flow passage cross-sectional area of the water passage W in the portion A having a temperature equal to or higher than the temperature is made larger than the flow passage cross-sectional area on the upstream side of the portion A, the water temperature at the outlet portion of the water passage W is equal to or higher than a predetermined temperature. The flow passage cross-sectional area of the water passage W in the portion A (that is, the portion at which the water temperature at which calcium carbonate as a scale component is deposited) is
Since it is larger than the flow passage cross-sectional area on the upstream side of the portion A, even if the scale component adheres to the pipe wall in the portion A, the time until the water passage W is closed can be lengthened. On the contrary, in the upstream portion of the water passage W where the water temperature is low and the heat transfer coefficient of water is low, the flow passage cross-sectional area is reduced and the flow velocity is increased, so that the heat exchange performance can be improved. it can.

[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 a plan view of a heat exchanger according to a second embodiment of the present invention.

FIG. 3 is a plan view of a heat exchanger according to a third embodiment of the present invention.

FIG. 4 is an enlarged plan view of an essential part of a heat exchanger according to a fourth embodiment of the present invention.

5 is a sectional view taken along line VV of FIG.

FIG. 6 is a plan view of a heat exchanger according to a fifth embodiment of the present invention.

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

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

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

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

FIG. 11 is a side view of the heat exchanger according to the tenth embodiment of the present invention.

FIG. 12 is a top view of the heat exchanger according to the tenth embodiment of the present invention.

FIG. 13 is a bottom view of the heat exchanger according to the tenth embodiment of the present invention.

FIG. 14 is a characteristic diagram showing a solubility curve of calcium carbonate.

[Explanation of symbols]

1 is a core tube, 2 is a winding tube, 5 is a U-shaped passage, 6 is a manifold, 8 is a water inlet, 9 is a water outlet, 14 is a scale adhesion promoting means, 17 and 18 are connecting portions, P and P'are Winding pitch, R
Is a refrigerant passage and W is a water passage.

Front page continuation (51) Int.Cl. ⁷ identification code FI theme code (reference) F28D 7/04 F28D 7/08 7/08 F28F 19/00 501Z (72) Inventor Haruo Nakata 1304 Kanaoka-cho, Sakai-shi, Osaka Address Daikin Industries, Ltd. Sakai Plant Kanaoka Factory F-term (reference) 3L036 AA04 AA46 3L103 AA20 BB43 CC02 CC28 DD03

Claims (18)

[Claims] 1. A core tube (1) constituting a water passage (W),
The core tube (1) and a winding tube (2) spirally wound around the core tube (1) to form a refrigerant passage (R), and water flowing through the water passage (W) flows through the refrigerant passage (R). A heat exchanger configured to be heated by a refrigerant, the winding pitch of the winding tube (2) at a portion (A) at an outlet portion of the water passage (W) where the water temperature is equal to or higher than a predetermined temperature. A heat exchanger characterized in that (P ') is made larger than a winding pitch (P) on the upstream side of the portion (A). 2. A core tube (1) constituting a water passage (W),
The core tube (1) and a winding tube (2) spirally wound around the core tube (1) to form a refrigerant passage (R), and water flowing through the water passage (W) flows through the refrigerant passage (R). A heat exchanger configured to be heated by a refrigerant, wherein the winding tube (2) in a portion (A) at an outlet portion of the water passage (W) where the water temperature is equal to or higher than a predetermined temperature is A heat exchanger characterized by being made parallel to the tube axis of the core tube (1). 3. A core tube (1) which is formed in a spiral shape and constitutes a water passage (W), and a winding which is spirally wound around the outer periphery of the core tube (1) and constitutes a refrigerant passage (R). A heat exchanger comprising a pipe (2) and configured to heat water flowing in the water passage (W) by a refrigerant flowing in the refrigerant passage (R), which is a spiral of the core pipe (1). A heat exchanger characterized in that a water inlet (8) is provided on the center side and a water outlet (9) is provided on the outer circumferential side of the spiral in the core tube (1). 4. A core tube (1) which is formed in a spiral shape to form a water passage (W), and a winding which is spirally wound around the outer periphery of the core tube (1) to form a refrigerant passage (R). A heat exchanger comprising a pipe (2) and configured to heat the water flowing through the water passage (W) by the refrigerant flowing through the refrigerant passage (R), the outlet of the water passage (W) ( 9) is provided on the outer peripheral side of the spiral in the core tube (1). 5. A core tube (1) formed in the spiral shape.
A plurality of stages are stacked so as to form one continuous water passage (W), and the final outlet (9) of the water passage (W) is provided on the outer peripheral side of the spiral in the core tube (1). The heat exchanger according to claim 4, wherein the heat exchanger is a heat exchanger. 6. The inlet (8) of the water passage (W) is provided on the outer peripheral side of the spiral in the core tube (1),
The heat exchanger according to claim 5, wherein the water passage (W) is communicated with the core tube (1) on the center side of the spiral. 7. The winding pitch (P ′) of the winding tube (2) in the portion (A) at the outlet portion of the water passage (W) where the water temperature is equal to or higher than a predetermined temperature is set to the portion (A). ) The heat exchanger according to any one of claims 3, 4, 5 and 6, wherein the winding pitch (P) on the upstream side is larger than the winding pitch (P). 8. The winding tube (2) in the portion (A) at the outlet portion of the water passage (W) where the water temperature is equal to or higher than a predetermined temperature is provided along the core tube (1). 4. The pipe according to claim 3, characterized in that it is parallel to the pipe axis of the pipe (1).
The heat exchanger according to any one of 4, 5, and 6. 9. The core tube (1) is provided along the outer side of the core tube (1) with the winding tube (2) in the curved portion (1a) of the core tube (1) included in the portion (A). 9. The heat exchanger according to claim 8, wherein the heat exchanger is parallel to the tube axis of FIG. 10. The flow passage cross-sectional area of the water passage (W) at the outlet portion of the water passage (W) where the water temperature is equal to or higher than a predetermined temperature is calculated from the portion (A). The heat exchanger according to any one of claims 1, 2, 3, 4, 5, 6, 7, 8 and 9, wherein the heat exchanger has a larger flow passage cross-sectional area on the upstream side. 11. A core tube (1) constituting a water passage (W).
And a winding tube (2) spirally wound around the core tube (1) to form a refrigerant passage (R), and water flowing through the water passage (W) is supplied to the refrigerant passage (R). A heat exchanger configured to be heated by a refrigerant flowing through the water passageway (W) at the outlet portion of the water passageway (W) where the water temperature is equal to or higher than a predetermined temperature. A heat exchanger characterized in that the flow passage cross-sectional area is made larger than the flow passage cross-sectional area on the upstream side of the portion (A). 12. A plurality of core tubes (1), (1), ... Having a predetermined length arranged in parallel, 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 the U-shaped passages (5), (5). The water passage (W) is formed, and the winding pipes (2), (2), ... Are connected via a winding pipe connecting portion (7) to form a series of refrigerant passages (R). Passage (W)
A heat exchanger configured to heat the water flowing through it by the refrigerant flowing through the refrigerant passage (R) so that the inner volume of each U-shaped passage (5) is increased to function as a scale adhering tank. A heat exchanger characterized in that 13. The manifold (6) includes each U
The heat exchanger according to claim 12, further comprising a scale adhesion promoting means (14) for promoting scale adhesion to the character-shaped passage (5). 14. The scale adhesion promoting means (14)
14. The heat exchanger according to claim 13, wherein is a high temperature refrigerant before being supplied to the refrigerant passage (R). 15. Heat exchanger according to claim 12, 13 or 14, characterized in that the manifold (6) is replaceable. 16. The winding pitch (P ′) of the winding tube (2) in the portion (A) at the outlet of the water passage (W) where the water temperature is equal to or higher than a predetermined temperature is set to the portion (A). )
The winding pitch (P) on the more upstream side is set to be larger than the winding pitch (P).
The heat exchanger according to claim 1. 17. The winding tube (2) in the portion (A) at the outlet of the water passage (W) where the water temperature is equal to or higher than a predetermined temperature is parallel to the axis of the core tube (1). Claims 12, 13, 14 and 1 characterized in that
The heat exchanger according to claim 5. 18. The flow passage cross-sectional area of the water passage (W) at the outlet portion of the water passage (W) where the water temperature is equal to or higher than a predetermined temperature is calculated from the portion (A). The heat exchanger according to any one of claims 12, 13, 14, 15, 16 and 17, wherein the heat exchanger has a larger flow passage cross-sectional area on the upstream side.