JP2006336885A - Heat exchanger and its manufacturing method - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger and its manufacturing method, capable of substantially enlarging a contact area effective for transferring heat to water piping and refrigerant piping, reducing contact heat resistance, improving efficiency of fins, and substantially improving heat exchanging performance by synergic effect such as turbulence promotion. <P>SOLUTION: This heat exchanger comprises the water piping for heat exchange obtained by connecting a plurality of water pipes 2 on which trough portions of plural lines of crest and trough portions are continuously and spirally formed by each line on an outer periphery of an area excluding both end portions, and the refrigerant piping 5 wound along the trough portions of the crest and trough portions of the water piping for heat exchange, and further continuously wound on connecting portions 4. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a heat exchanger for promoting heat exchange between water and a refrigerant, such as a heat exchanger for a heat pump water heater, and a method for manufacturing the same.

Conventional heat exchangers between water and refrigerant mainly have a triple structure using a double pipe having a leakage detection groove in order to avoid mixing of refrigerant and water due to corrosion of piping or the like. However, not only is the manufacturing process complicated and expensive, but there is also a limit to improving the performance of the heat exchanger, such as the length of the refrigerant pipe is limited due to the low degree of freedom in bending and the like.
In order to solve such a problem, the heat which the refrigerant pipe | tube with which a refrigerant | coolant distribute | circulates around the outer periphery of the core pipe (water pipe | tube) through which water distribute | circulates spirally, or was heat-transfer-coupled in parallel with the water pipe | tube. An exchanger has been proposed (see, for example, Patent Document 1).

JP 2002-228370 A (pages 2 to 3, FIGS. 3, 5, and 7)

  As in the invention of Patent Document 1, in the heat exchanger in which the refrigerant pipe is spirally wound around the outer periphery of the water pipe, since the outer periphery of the water pipe is smooth, the contact area between the water pipe and the refrigerant pipe is small. There was a problem that the thermal performance was not sufficient. There is also a proposal that a corrugated pipe is used as a water pipe. In general, a corrugated pipe is a pipe in which a continuous groove is spirally formed by pressing a tool against the outer circumference of a smooth pipe, and the outer circumference is reversed. Although it has an arc shape and shallow valleys, it is effective in promoting turbulent water flow, but the contact area between the water pipe and the refrigerant pipe is still small, and the heat transfer performance is not sufficient.

  In addition, when the refrigerant pipe is fitted into the arc-shaped recess of the corrugation of the water pipe, surface contact is made only by matching the curvature of the arc-shaped recess completely with the curvature of the refrigerant pipe. If the curvature of the concave portion is not larger than the curvature of the refrigerant pipe, it cannot be inserted to the back, so it is rather close to line contact, and it has been difficult to remarkably improve the contact heat transfer area.

  Further, when the water pipe is processed into a corrugated shape, there is a problem that if the water pipe is made long, the processing machine becomes large and the cost becomes high. For this reason, when a plurality of short water pipes subjected to corrugation are connected to form the entire length of the heat exchanger, it is necessary to join a refrigerant pipe spirally wound around the outer circumference of the water pipe for each water pipe.

  That is, since a plurality of refrigerant pipes are connected to a plurality of water pipes wound around a corrugated recess and wound in a flat spiral shape to form a heat exchanger, a plurality of water pipe connections are made at the intermediate portion thereof. And there are a plurality of refrigerant pipe connecting portions in the vicinity of the water pipe connecting portion. The refrigerant pipes are connected by brazing using connecting members obtained by cutting a brass material.

  As described above, since the heat exchanger of Patent Document 1 has a large number of connection points between the water pipe and the refrigerant pipe, not only the cost is increased, but also leakage of the refrigerant from the brazing portion, clogging of the brazing material, and the like occur. There was a problem that it was easy and reliability was lowered. Further, since a space required for joining the refrigerant pipes is required, there are many problems such as difficulty in making the heat exchanger compact.

  The present invention has been made in order to solve the above-described problems, and greatly increases the contact area effective for heat transfer between the water pipe and the refrigerant pipe, while reducing the contact thermal resistance, improving the fin efficiency, The heat exchange performance can be remarkably improved by synergistic effects such as flow promotion, and further, by eliminating the joint part of the refrigerant pipe in the middle of the heat exchanger, the cost increase is suppressed and the reliability is ensured. It is an object of the present invention to provide a heat exchanger that can be made compact and a manufacturing method thereof.

  The heat exchanger according to the present invention is a water for heat exchanging formed by connecting a plurality of water pipes in which the valleys of a plurality of peaks and valleys are continuously formed spirally for each stripe on the outer periphery of the region excluding both ends. The pipe is provided with a refrigerant pipe wound around the valley of the valley of the water pipe for heat pipe and continuously wound around the connecting portion.

  Moreover, the manufacturing method of the heat exchanger according to the present invention includes a plurality of water pipes in which a plurality of ridges and valleys are continuously formed for each line on the outer periphery of a region excluding both ends, and a water pipe for heat exchange. Is formed, and the refrigerant pipe is wound along the valley portion of the ridge and valley from one end of the water pipe for heat exchange, and is continuously wound to the other end by winding around the connection portion of the water pipe.

  According to the heat exchanger according to the present invention, the contact heat transfer area between the water pipe and the refrigerant pipe can be greatly expanded, and the heat transfer performance is greatly improved in combination with the effect of promoting turbulent flow and the effect of fin efficiency. Can be improved. In addition, because it has excellent flexibility for bending, etc., it has a high degree of freedom in shape. In addition, since there is no connection part of the refrigerant pipe in the middle of the heat exchanger, it is compact and can ensure reliability at low cost. A high-performance heat exchanger can be obtained.

[Embodiment 1]
1 is an exploded perspective view of a hot water supply outdoor unit equipped with a heat exchanger according to Embodiment 1 of the present invention, and FIG. 2 is a piping system diagram of the refrigeration cycle circuit and hot water supply circuit of FIG.
A heat exchanger unit 11 is disposed at the lowermost stage of the hot water supply outdoor unit, and a blower 22 for sending air to exchange heat between the evaporator 21 and the outside air is disposed above the heat exchanger unit 11. In addition, a compressor 23 is installed adjacent to the blower 22 in the upper part of the heat exchanger unit 11, and a pump 24 that circulates water in the hot water supply circuit is arranged in front of the right side, and a hot water supply tank (not shown). Water is taken into the indoor unit via the water inlet valve 25 and returns to the hot water supply tank from the hot water outlet valve 29 via the water pipe 2 of the heat exchanger 1 provided in the heat exchanger unit 11.

  The outer shell includes a grille 19 on the front, a front panel 18 having an air inlet on the left side, a back panel 20 that covers from the right side to the end of the evaporator 21, and a service panel 26 that covers valves. A top panel 17 is disposed at the top.

In the hot water supply equipment configured as described above, the heated gas refrigerant that has become high temperature and high pressure by the compressor 23 flows into the refrigerant pipe 5 of the heat exchanger 1 and is taken in from the water inlet valve 25 by the pump 24. When the water passes through the water pipe 2 of the heat exchanger 1, heat is exchanged to heat the water, and the water returns to the hot water tank through the hot water outlet valve 29.
In addition, the refrigerant that has transferred heat to the water is decompressed by the throttle valve 28 and flows into the evaporator 21, absorbs heat from the outside air blown by the blower 22, is evaporated and is reheated by the internal heat exchanger 15. The process returns to the compressor 23. The flow rate of the high-pressure refrigerant flowing into the internal heat exchanger 15 is adjusted by the flow rate adjustment valve 27.

3 is a perspective view showing the configuration of the heat exchanger unit, FIG. 4 is an explanatory view of the heat exchanger of FIG. 3, FIG. 5 is an explanatory view of the water pipe of FIG. 4, and FIG. 6 is a water pipe of FIG. It is explanatory drawing which shows the state which wound refrigerant | coolant piping.
The water pipe 2 has a plurality of (for example, 2 to 4) crests 3a and troughs 3b alternately provided on the outer periphery, and crests 3a are continuously provided in a spiral manner for each of the crests. A smooth part (connecting part) without the mountain-and-valley part 3 is formed at both ends, and the end part of one smoothing part is expanded in a bag shape so that the smoothing part of the subsequent water pipe 2 can be inserted and connected. Yes.

  In addition, the inlet refrigerant pipe 7 is branched into a plurality of refrigerant pipes 5 through the connection parts 6a, is fitted into the valley parts 3b for each strip provided on the outer periphery of the water pipe 2, and is wound over the entire length. It is connected to the outlet refrigerant pipe 8 through a connecting portion 6b that joins.

  The water pipe 2 around which the plurality of refrigerant pipes 5 are wound in this way is formed in a substantially elliptical elliptical coil shape, and the connection part 4 is located in the straight line part. The water flowing through the water pipe 2 and the refrigerant flowing through the refrigerant pipe 5 are configured to face each other. The water pipe 2 around which the refrigerant pipe 5 is continuously wound is as shown in FIG. 6, and has an appearance in which the crest 3a of the water pipe 2 and the refrigerant pipes 5a, 5b, 5c of a plurality of paths can be seen alternately.

Next, a method for manufacturing the heat exchanger 1 according to the present embodiment will be described with reference to FIG.
FIG. 7 (a) shows a state before connection of the plurality of water pipes 2a, 2b,..., FIG. 7 (b) shows a state after connection, and the connection portion 4 is metal-bonded by brazing or the like, Such a connection is repeated until the full length of the heat exchanger 1 is reached. Hereinafter, a water pipe that is connected to the plurality of water pipes 2a, 2b,... And constitutes the entire length of the heat exchanger is referred to as a heat exchange water pipe.

  When the connection of the water pipe 2 is finished, as shown in FIG. 7 (c), a plurality of paths (in the drawing) are provided along each valley 3b of the mountain valley 3 provided on the outer periphery of the water pipe 2a at one end. Is wrapped around the refrigerant pipes 5a, 5b, 5c, and the refrigerant pipes 5a, 5b, 5c are also wound around the connection part 4 without the mountain valley part 3. Next, as shown in FIG. 7 (d), winding is continuously performed along each valley 3b of the water pipe 2b connected thereto, and such work is repeated up to the final water pipe 2n.

  In this way, the heat exchanger 1 in which the refrigerant pipes 5a, 5b, 5c are wound over the entire length of the water exchange water pipe to which the plurality of water pipes 2a, 2b,..., 2n are connected is as shown in FIG. After being bent into a plurality of elliptical coils in the vertical direction, the water pipe 2 and the refrigerant pipe 5 are integrally joined with a low melting point metal such as solder. At this time, the length of the single piece of the water pipe 2 is set in advance so that the connection part 4 of the water pipe 2 is positioned at the straight part of the elliptical coil shape.

According to this Embodiment comprised as mentioned above, since there is no connection part of the refrigerant | coolant piping 5 other than the inlet_port | entrance and exit of the heat exchanger 1, the connection location of the refrigerant | coolant piping 5 reduces significantly. For this reason, there is almost no refrigerant leakage from the brazing part of the connecting part and clogging of the brazing material, so that not only the reliability is improved, but also the brazing processing cost can be reduced. Further, since the refrigerant pipe 5 is not suddenly expanded or contracted, the flow loss of the refrigerant can be reduced and the heat transfer area of the refrigerant pipe 5 wound around the water pipe 2 is increased, so that the heat transfer performance is improved.
Furthermore, since the space required for the connection of the refrigerant pipe 5 becomes unnecessary, the heat exchanger 1 can be made compact. Moreover, since the connection part 4 of the water piping 2 is located in the linear part of an ellipse coil shape, the water leak from a brazing part can be prevented and reliability improves.

[Embodiment 2]
FIG. 8 is an explanatory view of a heat exchanger according to Embodiment 2 of the present invention, and FIG. 9 is an explanatory view of a manufacturing method thereof. In addition, the same part as Embodiment 1 attaches | subjects the same code | symbol as this, and abbreviate | omits description.
In the present embodiment, the water pipe 2 in which the refrigerant pipes 5a, 5b, 5c are wound around the valley portions 3b of the plurality of mountain valley portions 3 provided on the outer periphery is formed into a flat and substantially elliptical oval spiral shape. It is. In addition, the connection part 4 of the water piping 2 is located in an oval spiral linear part, and it is comprised so that water and a refrigerant | coolant may become a counterflow.

  In the manufacture of the heat exchanger 1 according to the present embodiment, first, as shown in FIG. 9A, a plurality of ridges and valleys 3 provided on the outer periphery (the case of three is shown in the figure). As shown in FIG. 9B, the second water pipe 2b is connected to the first water pipe 2a in which the three-pass refrigerant pipes 5a, 5b, and 5c are wound around the valley portion 3b, and brazed or the like. To join the metal. Then, as shown in FIG. 9 (c), the refrigerant pipes 5a, 5b, 5c are wound around the connection part 4, and subsequently, as shown in FIG. 9 (d), the valley part of the second water pipe 2b. Wind around 3b to the rear end.

Then, the first and second water pipes 2a and 2b are bent so as to form part of the elliptical spiral shape of FIG. Then, as shown in FIG. 9 (b) again, the third water pipe is connected to the second water pipe 2b, and the refrigerant pipes 5a, 5b, 5c are wound around the valley part 3b from the connecting part 4 and sequentially bent. Process.
Such an operation is repeated until the full length is reached, and the flat oval spiral heat exchanger 1 is formed. Then, after the bending process is completed over the entire length, the water pipe 2 and the refrigerant pipes 5a, 5b, 5c are integrally joined with a low melting point metal such as solder.

  According to the present embodiment, since the water pipe 2 around which the refrigerant pipe 5 is wound is sequentially bent, it is not necessary to hold the heat exchanger 1 in a long state over the entire length of the heat exchanger 1, so that the processing equipment can be shortened. This can reduce processing costs. Other actions and effects are the same as those in the first embodiment.

[Embodiment 3]
10 is a cross-sectional view of a main part of a heat exchanger according to Embodiment 3 of the present invention, and FIG. 11 is a partially enlarged view of FIG. The same parts as those in the first embodiment are denoted by the same reference numerals.
In this embodiment, the water pipe 2 provided with a plurality of ridges and valleys 3 provided on the outer periphery (three cases are shown in the figure) continuously spirally for each row is provided with three passes. The refrigerant pipes 5a, 5b, 5c are spirally wound along the valleys 3b of the respective strips to enlarge the contact area between the water pipe 2 and the refrigerant pipes 5a, 5b, 5c. In the present embodiment, the valley portion 3b of the mountain valley portion 3 is formed in a substantially inverted trapezoidal shape.

Then, with respect to the flow direction of water in the water pipe 2 (indicated by arrows), the refrigerant branched at the inlet flows in the opposite direction so as to be spirally opposed in the refrigerant pipes 5a, 5b, 5c, It merges again at the exit and becomes one. In this case, CO ₂ , HFC, HCFC, HC, H ₂ O, or the like can be used as the refrigerant, but the refrigerant is not limited to this.

In FIG. 11, the height H of the crest 3 a of the crest 3 provided on the outer periphery of the water pipe 2 is set to be not less than the radius R _o / 2 and not more than the diameter R _o of the refrigerant pipe 5. That is, the height of the crest 3a is made larger than the radius R _o / 2 of the refrigerant pipe 5 in order to stably secure the contact area between the crest 3c of the valley 3b and the refrigerant pipe 5. . Further, the spiral pitch P of the crest 3a is equal to or less than 2 times the diameter R _o at least the diameter R _o of the refrigerant pipe 5.

  As described above, the refrigerant pipe 5 is wound around the outer periphery of the water pipe 2 at the pitch P in the specific range and at the height H of the peak part 3a in the specific range, so that the mountain valley part 3 serves as a guide. Thus, the refrigerant pipe 5 can be easily wound and fixed at a predetermined position, and excessive flattening and buckling of the refrigerant pipe 5 can be prevented.

Furthermore, the width B of the bottom 3d of the valley portion 3b of the peaks and valleys portion 3, at least the inside diameter R _i of the refrigerant pipe 5, and the following outer diameter R _o + 0.24 mm. Thus, by setting the width B of the valley 3b to be equal to or larger than the inner diameter R _i of the refrigerant pipe 5 by inserting an inner diameter mandrel or the like, the refrigerant pipe 5 is surely in contact with the bottom 3d of the valley 2b, and the refrigerant pipe 5 Since the pressing force to the bottom 3d is easily generated by the tension at the time of winding, the contact thermal resistance can be reduced.

In this embodiment, the height H of the ridges 3a of the peaks and valleys portion 3 provided on the outer circumference of the water pipe 2 is too high than a diameter R _o of the refrigerant pipe 5, space efficiency of the heat exchanger is deteriorated converting mechanism prevents the compact, the pitch P of the crest 3a can not be fitted the refrigerant pipe 5 that it follows the diameter R _o of the refrigerant pipe 5 deep valleys 3b, Thus, the refrigerant pipe 5 is valley Since the bottom 3d of 3b cannot be contacted, the contact heat transfer area between the refrigerant pipe 5 and the water pipe 2 is reduced, and the original purpose cannot be achieved. If the pitch P of the crest 3a is too large and exceeds twice the diameter _Ro of the refrigerant pipe 5, the total length of the refrigerant pipe 5 with respect to the unit length of the water pipe 2 becomes short. This is not preferable because the performance is reduced.

Further, in the present embodiment, even when the contact area between the valley 3b of the water pipe 2 and the refrigerant pipe 5 is enlarged by brazing or the like, the gap between the mountain side inclined surface 3c of the valley 3b and the refrigerant pipe 5 is increased. A brazing gap can be designed. In general, in order to ensure brazing quality, it is desirable in terms of work that the brazing gap is 0.08 mm to 0.12 mm. For this reason, the gap between the refrigerant pipe 5 and the ridge-side inclined surface 3c is formed on both sides. well 0.24mm Tosureba from 0.16 mm, therefore, the width B of the bottom 3d of the valley 3b is preferred if the diameter R _o + 0.16~0.24mm the refrigerant pipe 5. Thereby, the contact area of the trough part 3b and the refrigerant | coolant piping 5 can be expanded with few brazing materials.

In addition, as shown in FIG. 10, the mountain valley portion 3 provided on the outer periphery of the water pipe 2 has a shape in which turbulent flow is likely to occur inside the water pipe 2. Can be improved.
Furthermore, since the peak part 3a of the peak part 3 provided in the water piping 2 acts also as a heat exchange fin, thermal conductivity improves by the fin efficiency improvement effect.

  According to the present embodiment, the refrigerant pipe 5 is in contact with the bottom 3d of the valley 3b provided on the outer periphery of the water pipe 1, and the minimum gap portion between the mountain side inclined surface 3c of the valley 3b and the refrigerant pipe 5 is used. However, since contact is made directly or by brazing or the like, there are three contact portions and heat transfer is joined. For this reason, the effective contact heat transfer area can be expanded more than three times compared to the heat exchanger in which the refrigerant pipe is wound around the conventional smooth water pipe, and therefore the above-described turbulent flow promotion effect and fin efficiency improvement. As a synergistic effect, AK value (heat transfer area × heat passage rate) per unit water pipe length can be greatly improved.

Here, the water pipe 2 was manufactured by fixing both ends of the phosphorous deoxidized copper smooth pipe, inserting a mandrel on the inner diameter side, and adding a twisting process, but the invention is not limited to this. The water pipe 2 may be manufactured by other pipe processing techniques such as processing, cast forging, cutting, and rolling. Moreover, if the raw material of the water pipe 2 is an internally grooved pipe, a suitable effect can be obtained.
Further, the material of the water pipe 2 and the refrigerant pipe 5 is not limited to phosphorous deoxidized copper, and pipe metals such as copper, aluminum, iron, stainless steel, titanium, or alloys thereof are used depending on the application. May be.
Examples of the present embodiment will be described below.

The water pipe 2 has an outer diameter SR _o : 14.0 mm, an inner diameter SR _i : 8.0 mm, a number of ridges: 4, a height H of the mountain part 3a: 2.5 mm, and a mountain part 3a. Pitch P: 4.8 mm, bottom portion 3d width B: 3.0 mm, refrigerant pipe 5 has outer diameter R _o : 3.2 mm, inner diameter R _i : 2.0 mm, and refrigerant has four passes And there is no brazing.
In this embodiment, by setting the dimensional relationship between the crest and valley portion 3 of the water pipe 2 and the refrigerant pipe 5 to be indented, a relatively excellent heat transfer performance is exhibited without brazing between them. did it.

The water pipe 2 has an outer diameter SR _o : 14.0 mm, an inner diameter SR _i : 8.0 mm, the number of ridges: 3, the height H of the ridge 3a: 3.0 mm, the pitch P of the ridge 3a: 5.8 mm, Width B of the bottom portion 3d of the valley portion 3b: 3.5 mm, the refrigerant pipe 5 has an outer diameter R _o : 3.6 mm, an inner diameter R _i : 2.4 mm, the refrigerant has three passes, and a phosphor copper of φ0.8 Was spirally wound and brazed.

  In this example, heat transfer performance was further improved because heat transfer bonding was performed by brazing the heat transfer contact portion. In brazing, as shown in FIG. 12 (a), the gap between the crest 3a of the water pipe 2 and the refrigerant pipe 5, or the bottom of the trough 3b of the water pipe 2 as shown in FIG. 12 (b). A brazing material 9 or solder material or the like may be wound around the gap between 3d and the refrigerant pipe 5, and furthermore, as shown in FIG. 13, the bottom 3d of the valley 3b of the water pipe 2 and the refrigerant pipe 5 In the meantime, a ribbon-like brazing material 9 or a solder material can be appropriately wound.

Water pipe 2 has an outer diameter SR _o: 15.0 mm, inner diameter SR _i: 9.0 mm, Conditions: 2, crest 3a height H: 3.5 mm, crest 3a of the pitch P: 6.2 mm, The width B of the bottom portion 3d of the valley portion 3b is 4.0 mm, the refrigerant pipe 5 has an outer diameter R _o : 4.0 mm, an inner diameter R _i : 2.8 mm, the refrigerant has two passes, and a width: 3.5 mm. A ribbon-shaped solder material 9 having a thickness of 0.2 mm was set and soldered as shown in FIG.

Water pipe 2 has an outer diameter SR _o: 18.0 mm, inner diameter SR _i: 10.0 mm, Conditions: 4, crest 3a height H: 3.5 mm, crest 3a of the pitch P: 7.2 mm, As shown in FIG. 13, the width B of the bottom 3d of the valley 3b is 5.0 mm, the refrigerant pipe 5 has an outer diameter R _o : 5.0 mm, an inner diameter R _i : 4.0 mm, and the refrigerant has two passes. The ribbon-shaped low melting point metal 9 such as aluminum, solder, brazing material or the like is wound between and joined to the bottom 3 d of the valley 3 b of the water pipe 2 and the refrigerant pipe 5.

In Example 4, since a low melting point metal having high plastic deformation ability such as aluminum, solder, brazing material, etc. is sandwiched between the bottom 3d of the trough 3b of the water pipe 2 and the refrigerant pipe 5, the applied pressure If this is sufficient, similar to the case of Example 1, excellent heat transfer bonding can be realized without performing heat brazing. Although not shown in the embodiment, according to the experimental results, the outer diameter SR ₀ of the crest 3a of the crest 3 of the water pipe 2 is 1.5 times or more and 2.5 times or less than the inner diameter SR _i. The inner diameter SR _i of the water pipe 2 is preferably 8 mm or more and 12 mm or less.

  FIG. 14 is an explanatory view showing a state in which the refrigerant pipe 5 is heated and brazed to the valley 3b of the water pipe 2. FIG. Heat brazing can be performed by in-furnace brazing, high-frequency brazing, gas burner brazing, or the like. The same applies to soldering.

  According to the present embodiment, by appropriately setting the dimensions of the mountain valley portion 3 provided on the outer periphery of the water pipe 2 and the refrigerant pipe 5 wound around this, without brazing between them or both By interposing a low-melting-point metal with high plastic deformation ability such as aluminum, solder, brazing material in between, heat brazing is performed, or both are integrally joined by pressure, so heat transfer joining is performed. In particular, the productivity and quality can be improved remarkably, and excellent heat transfer performance can be exhibited. Needless to say, this embodiment can be applied to the first and second embodiments.

[Embodiment 4]
FIG. 15 is an explanatory diagram showing an example of the number of ridges and valleys provided on the outer periphery of the water pipe according to Embodiment 4 of the present invention and the path pattern of the refrigerant pipe wound around this.
15A shows an example in which the mountain valley portion 3 has two lines and the refrigerant pipe 5 has two passes, and FIG. 15B shows an example in which the mountain valley portion 3 has three lines and the refrigerant pipe 5 has three passes. ) Is an example in which the mountain valley portion 3 has three strips and the refrigerant pipe 5 has two passes, FIG. 15D shows an example in which the mountain valley portion 3 has four strips and the refrigerant pipe 5 has four passes, and FIG. 4 and an example in which the refrigerant pipe 5 has two passes is shown. As described above, the refrigerant pipes 5 branched into these 2 to 4 paths are integrated at the inlet and the outlet, and become one each.
The number of ridges and valleys 3 of the water pipe 2 and the number of passes of the refrigerant pipe 5 wound around the water pipe 2 can be suitably selected according to characteristics such as the flow rate, flow velocity, and pressure loss of the refrigerant.

  In the above description, the water pipe 2 around which the refrigerant pipe 5 is wound is bent and formed into an oval coil shape or an oval spiral shape. However, the present invention is not limited to this. The water pipe 2 around which the pipe 5 is wound may be bent and formed into a flat spiral shape (hereinafter referred to as a flat spiral shape).

  The heat exchanger according to the present invention described above is not limited to a heat exchanger for a heat pump type hot water heater, and can be widely applied to a heat exchanger related to water and a refrigerant. In addition, the heat exchanger which concerns on this invention can further improve heat exchange performance by winding a heat insulation tape around an outer periphery, or covering with a heat insulating material.

It is a disassembled perspective view of the hot water supply outdoor unit provided with the heat exchanger which concerns on Embodiment 1 of this invention. FIG. 2 is a piping system diagram of the refrigeration cycle circuit and hot water supply circuit of FIG. 1. It is a perspective view which shows the structure of the heat exchanger unit of FIG. It is explanatory drawing of the twisted tube type heat exchanger of FIG. It is explanatory drawing of the water piping of FIG. It is explanatory drawing which shows the state which wound the refrigerant | coolant piping around the water piping of FIG. 3 is an explanatory diagram of a method for manufacturing the heat exchanger according to Embodiment 1. FIG. It is explanatory drawing of the heat exchanger which concerns on Embodiment 2 of this invention. 6 is an explanatory diagram of a method for manufacturing a heat exchanger according to Embodiment 2. FIG. It is principal part sectional drawing of the heat exchanger which concerns on Embodiment 3 of this invention. FIG. 11 is a partially enlarged view of FIG. 10. FIG. 6 is an explanatory diagram of Example 2. It is explanatory drawing of Example 4. FIG. It is explanatory drawing which shows the state which joined the trough part of water piping, and refrigerant | coolant piping by heating brazing. It is explanatory drawing which shows the example of the path | route pattern of the refrigerant | coolant piping wound around this, and the number of the threads of the water piping which concern on Embodiment 4 of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Heat exchanger, 2 water piping, 3 mountain valley part, 3a mountain part, 3b valley part, 3c mountain part side inclined surface, 3d bottom part, 4 connection part, 5 refrigerant | coolant piping.

Claims (17)

A heat exchange water pipe formed by connecting a plurality of water pipes formed continuously in a spiral shape to the outer circumference of the region excluding both ends, and a plurality of crests and valleys,
A heat exchanger comprising: a refrigerant pipe wound around the valley of the valley of the water pipe for the heat pipe and continuously wound around the connecting part.   The heat exchanger according to claim 1, wherein a plurality of refrigerant pipes are wound around the heat exchange water pipe.   The water pipe for a heat exchanger around which the refrigerant pipe is wound is formed in an oval coil shape, an oval spiral shape, or a flat spiral shape, and the connection portion of the water pipe is positioned at the straight portion. Item 3. The heat exchanger according to item 1 or 2.   The heat exchanger according to any one of claims 1 to 3, wherein the water flowing through the heat exchange water pipe and the refrigerant flowing through the refrigerant pipe are opposed to each other.   The heat exchanger according to any one of claims 1 to 4, wherein an outer diameter of a peak portion of a mountain valley portion of the water pipe is 1.5 times or more and 2.5 times or less of an inner diameter thereof.   The heat exchanger according to any one of claims 1 to 5, wherein a height of a crest portion of the crest and trough portion of the water pipe is formed to be not less than 1/2 of the outer diameter of the refrigerant pipe and not more than the outer diameter. .   The heat exchanger according to any one of claims 1 to 6, wherein a peak n pitch of a mountain valley portion of the water pipe is formed to be not less than the outer diameter of the refrigerant pipe and not more than twice the diameter.   The width of the bottom part of the valley part of the valley part of the said water piping was formed in the outer diameter + 0.16mm-0.24mm or less more than the internal diameter of refrigerant | coolant piping, The one in any one of Claims 1-7 characterized by the above-mentioned. Heat exchanger.   The heat exchanger according to any one of claims 1 to 8, wherein a minimum gap formed between a crest-side inclined surface of a crest and a valley of the water pipe and the refrigerant pipe is heat-transferred.   The heat exchanger according to any one of claims 1 to 9, wherein a mountain valley portion of the water pipe and a refrigerant pipe wound around the water pipe are joined by a low melting point metal.   The thickness of the said water piping was 0.5 mm or more and 1.0 mm or less, The heat exchanger of Claims 1-10 characterized by the above-mentioned.   The heat exchanger according to claim 1, wherein an inner diameter of the water pipe is 8 mm or more and 12 mm or less.   The heat exchanger according to claim 1, wherein the refrigerant flowing through the refrigerant pipe is a carbon dioxide refrigerant.   A plurality of ridges and valleys connected to the outer periphery of the region excluding both ends are connected to a plurality of water pipes formed continuously for each stripe to form a heat exchange water pipe, and the ridges and valleys are formed from one end of the heat exchange water pipe. A method of manufacturing a heat exchanger, wherein a refrigerant pipe is wound along a trough portion of the section and is also wound around a connecting portion of the water pipe and continuously wound to the other end.   15. The heat exchanging water pipe around which the refrigerant pipe is wound is bent so that the connecting portion of the water pipe is located in a straight portion, and formed into an oval coil shape or an oval spiral shape. The manufacturing method of the heat exchanger of description.   A refrigerant pipe is wound from one end of a water pipe in which a plurality of valleys of valleys are continuously formed on the outer periphery of the region excluding both ends along the valley of the valleys, When the other end is reached, the next water pipe is connected to the water pipe, and the refrigerant pipe is wound around the connecting portion, and then wound around the valley of the next water pipe to the end along the valley. The heat exchanger manufacturing method characterized by repeating. The plurality of water pipes connected by winding the refrigerant pipe are bent, and the bent water pipes are connected so that the connecting parts are located in the straight part to form an elliptical coil shape or an elliptical spiral. The heat exchanger manufacturing method according to claim 16, wherein the heat exchanger is formed in a shape.

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