JPWO2019111349A1 - Manufacturing method of heat exchanger, refrigeration cycle device and heat exchanger - Google Patents

Abstract

The heat exchanger according to the present invention has a first pipe through which the first heat medium flows and a second pipe around which the second heat medium flows, which is wound around the first pipe. Has a plurality of protrusions protruding to the inner surface, and the protrusions are formed in a spiral shape in the direction in which the first heat medium flows through the first pipe, and each of the protrusions formed in one row. Are arranged at unequal intervals.

Description

The present invention relates to a heat exchanger including a first pipe and a second pipe wound around the first pipe, a refrigeration cycle device including the heat exchanger, and a method for manufacturing the heat exchanger. is there.

Conventionally, the first pipe in which the flow path through which the first heat medium flows is formed, and the second pipe in which the flow path through which the second heat medium flows is formed by being wound around the outer periphery of the first pipe. There is a heat exchanger equipped. In such a heat exchanger, heat exchange is performed between the first heat medium flowing through the first pipe and the second heat medium flowing through the second pipe. The first pipe may be referred to as a core pipe. The second pipe may be referred to as an outer pipe. Examples of the first heat medium include water and antifreeze. Examples of the second heat medium include a refrigerant.

As such, as described in Patent Document 1, "a core tube in which an outer surface is pressed to form a plurality of protrusions on the inner surface, and a winding tube wound around the outer surface of the core tube. A heat exchanger equipped with a "heat exchanger" has been proposed.

The heat exchanger described in Patent Document 1 includes a core tube in which a plurality of protrusions are formed on the inner surface by pressing the outer surface. By configuring the core tube in this way, in the heat exchanger described in Patent Document 1, the flow of the first heat medium flowing in the core tube is agitated by the protrusions, and the flow of the first heat medium flowing in the core tube is combined with water which is the first heat medium flowing through the core tube. The heat exchange performance with the refrigerant, which is the second heat medium flowing through the winding tube, is improved.

Japanese Unexamined Patent Publication No. 2006-317114

In the heat exchanger described in Patent Document 1, when the outer surface of the core tube is pressed to form a plurality of protrusions on the inner surface, a gear-shaped jig is used as a method for forming the protrusions, and the teeth of the gear are used. Is pressed against the outer surface of the core tube to form an inner protrusion in a spiral shape. In the following description, a jig having a gear shape is simply referred to as a jig. Further, in order to further improve the heat exchange performance by applying the protrusions, a large number of internal protrusions can be installed in the spiral direction by using a plurality of jigs. By operating the plurality of jigs independently, a plurality of protrusions will be formed.

When the protrusions are formed by a plurality of jigs, the positional relationship of the protrusions provided by each gear is determined by the phase difference of each gear. Depending on the phase difference of each jig, the protrusions provided by one jig and the protrusions provided by the other jigs may be installed so as to be aligned in the pipe axis direction. The protrusions installed on the upstream side in the flow of the first heat medium stir the flow of the first heat medium, and the heat exchange performance is improved. On the other hand, in the protrusions installed on the downstream side in the flow of the first heat medium, the flow velocity becomes smaller, the stirring effect becomes smaller, and the effect of improving the heat exchange performance by the protrusions becomes smaller.

The present invention has been made against the background of the above problems, and is a heat exchanger capable of improving heat exchange performance by not reducing the stirring effect in a plurality of protrusions, and heat exchange thereof. It is an object of the present invention to provide a refrigeration cycle apparatus equipped with a vessel and a method for manufacturing the heat exchanger thereof.

The heat exchanger according to the present invention has a first pipe through which a first heat medium flows and a second pipe around which a second heat medium flows, which is wound around the first pipe. The pipe has a plurality of protrusions protruding to the inner surface, and the protrusions are formed in a spiral shape in the direction in which the first heat medium flows through the first pipe, and are formed in one row. Each of the above-mentioned protrusions is arranged at unequal intervals.

According to the heat exchanger according to the present invention, since the adjacent protrusions do not overlap in the state where the first pipe is projected in the pipe axis direction, the flow velocity is increased even in the protrusions formed on the downstream side of the flow of the first heat medium. The heat exchange performance is improved without becoming smaller.

FIG. 5 is a schematic configuration diagram schematically showing an example of a circuit configuration of a refrigeration cycle apparatus provided with a heat exchanger according to a first embodiment of the present invention. It is a perspective view which shows schematic structure of the heat exchanger which concerns on Embodiment 1 of this invention. It is explanatory drawing for demonstrating an example of the formation of the protrusion of the 1st pipe of the heat exchanger which concerns on Embodiment 1 of this invention. It is explanatory drawing for demonstrating an example of the formation of the protrusion of the conventional 1st pipe as a comparative example. It is explanatory drawing for demonstrating the 1st pipe provided with the protrusion formed by the method of FIG. It is explanatory drawing for demonstrating the 1st pipe provided with the protrusion formed by the method of FIG. It is explanatory drawing for demonstrating another example of the formation of the protrusion of the 1st pipe which concerns on Embodiment 1 of this invention. It is explanatory drawing for demonstrating the interval of the protrusion of the 1st pipe of the heat exchanger which concerns on Embodiment 1 of this invention. It is explanatory drawing for demonstrating the interval of the protrusion of the 1st pipe of the heat exchanger which concerns on Embodiment 1 of this invention. It is explanatory drawing for demonstrating the shape of the 1st pipe of the heat exchanger which concerns on Embodiment 2 of this invention. It is explanatory drawing for demonstrating the shape of the 1st pipe of the heat exchanger which concerns on Embodiment 3 of this invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings as appropriate. In the following drawings including FIG. 1, the relationship between the sizes of the constituent members may differ from the actual one. Further, in the following drawings including FIG. 1, those having the same reference numerals are the same or equivalent thereof, and this shall be common to the entire text of the specification. Furthermore, the forms of the components represented in the full text of the specification are merely examples, and are not limited to these descriptions.

Embodiment 1.
FIG. 1 is a schematic configuration diagram schematically showing an example of a circuit configuration of a refrigeration cycle device 200 provided with a heat exchanger 100 according to a first embodiment of the present invention. The refrigeration cycle apparatus 200 will be described with reference to FIG.
In the first embodiment, it is assumed that the first heat medium is water and the second heat medium is a refrigerant.

<Overall configuration of refrigeration cycle device 200>
The refrigeration cycle device 200 includes a refrigerant circuit A1 and a heat medium circuit A2. The refrigerant circuit A1 and the heat medium circuit A2 are thermally connected via the heat exchanger 100. Further, the heat medium circuit A2 is connected to the water supply circuit A3 via the hot water storage tank 207. The water supply circuit A3 is connected to the hot water supply utilization unit U and is configured to supply hot water to the hot water supply utilization unit U. The hot water supply utilization unit U includes at least one of various loads that require hot water, such as a faucet and a bath for a household water supply. The water supply circuit A3 is connected to a water pipe or the like so that water can be supplied.

Refrigerant circulates in the refrigerant circuit A1 via the refrigerant pipe 20A. Carbon dioxide can be used as the refrigerant. The refrigerant circuit A1 is formed by including a compressor 201 that compresses the refrigerant, a heat exchanger 100 that functions as a condenser, a drawing device 202, and a heat exchanger 203 that functions as an evaporator.

The compressor 201 compresses the refrigerant. The refrigerant compressed by the compressor 201 is discharged from the compressor 201 and sent to the heat exchanger 100. The compressor 201 can be composed of, for example, a rotary compressor, a scroll compressor, a screw compressor, a reciprocating compressor, or the like.

The heat exchanger 100 functions as a condenser and exchanges heat between the high-temperature and high-pressure refrigerant flowing through the refrigerant circuit A1 and the water flowing through the heat medium circuit A2 to heat the water and condense the refrigerant. is there. The heat exchanger 100 is a water-refrigerant heat exchanger that exchanges heat between water and a refrigerant. The heat exchanger 100 will be described in detail later.
The heat exchanger 100 corresponds to the heat exchanger of the present invention.

The throttle device 202 expands the refrigerant flowing out of the heat exchanger 100 to reduce the pressure. The throttle device 202 may be composed of, for example, an electric expansion valve whose flow rate of the refrigerant can be adjusted. As the throttle device 202, not only an electric expansion valve but also a mechanical expansion valve using a diaphragm for a pressure receiving portion, a capillary tube, or the like can be applied.

The heat exchanger 203 functions as an evaporator and exchanges heat between the low-temperature low-pressure refrigerant flowing out of the throttle device 202 and the air supplied by the blower 203A attached to the heat exchanger 203 to exchange heat with the low-temperature low-pressure refrigerant. It evaporates a liquid refrigerant or a two-phase refrigerant. The heat exchanger 203 can be composed of, for example, a fin-and-tube heat exchanger, a microchannel heat exchanger, a heat pipe heat exchanger, or the like.

Water circulates in the heat medium circuit A2 via the heat medium pipe 10A. The heat medium circuit A2 is formed by including a heat exchanger 100 and a pump 205 that conveys water.

Further, the refrigeration cycle device 200 includes a control device 60 that controls the entire refrigeration cycle device 200. The control device 60 controls the drive frequency of the compressor 201. Further, the control device 60 controls the opening degree of the throttle device 202 according to the operating state. Further, the control device 60 controls the drive of the blower 203A and the pump 205. That is, the control device 60 uses the information sent from each temperature sensor (not shown) and each pressure sensor (not shown) based on the operation instruction, and uses the compressor 201, the throttle device 202, the blower 203A, the pump 205, and the like. Control each actuator of.

Each functional unit included in the control device 60 is composed of dedicated hardware or an MPU (Micro Processing Unit) that executes a program stored in a memory.

<Structure of heat exchanger 100>
FIG. 2 is a perspective view schematically showing the configuration of the heat exchanger 100.
In the heat exchanger 100, a first pipe 1 in which a first flow path FP1 through which water as a first heat medium flows is formed, and a second flow path FP2 in which a refrigerant as a second heat medium flows are formed. It also has a second pipe 2. The second pipe 2 is wound around the outer circumference of the first pipe 1 in one or more rows and is in contact with the first pipe 1. The first pipe 1 constitutes a part of the heat medium pipe 10A. The second pipe 2 constitutes a part of the refrigerant pipe 20A.

The first pipe 1 is formed with a water inlet 1a and a water outlet 1b communicating with the first flow path FP1. Further, the second pipe 2 is formed with a refrigerant inflow port 2a and a refrigerant outflow port 2b communicating with the second flow path FP2.
The heat exchanger 100 can be connected to the refrigerant circuit A1 and the heat medium circuit A2 so that the direction of the water flowing through the first pipe 1 and the direction of the refrigerant flowing through the second pipe 2 face each other. As a result, the heat exchange efficiency between the heat medium and the refrigerant is improved.

<Operation of refrigeration cycle device 200>
Here, returning to FIG. 1, the operation of the refrigeration cycle apparatus 200 will be described.
The refrigeration cycle device 200 is capable of hot water supply operation based on an instruction from the load side.
The operation of each actuator is controlled by the control device 60.

The low-temperature and low-pressure refrigerant is compressed by the compressor 201, becomes a high-temperature and high-pressure gas refrigerant, and is discharged from the compressor 201. The high-temperature and high-pressure gas refrigerant discharged from the compressor 201 flows into the heat exchanger 100. The refrigerant that has flowed into the heat exchanger 100 flows through the second pipe 2 and exchanges heat with the water flowing through the first pipe 1. At this time, the refrigerant is condensed into a low-temperature, high-pressure liquid refrigerant that flows out of the heat exchanger 100. When carbon dioxide is used as the refrigerant, the temperature of the refrigerant changes while remaining in the supercritical state.
On the other hand, the water that has flowed into the first pipe 1 is heated by the refrigerant flowing through the second pipe 2 and is supplied to the load side.

The low-temperature and high-pressure liquid refrigerant flowing out of the heat exchanger 100 becomes a low-temperature and low-pressure liquid refrigerant or a two-phase refrigerant by the drawing device 202, and flows into the heat exchanger 203. The refrigerant that has flowed into the heat exchanger 203 exchanges heat with the air supplied by the blower 203A attached to the heat exchanger 203, becomes a low-temperature low-pressure gas refrigerant, and flows out of the heat exchanger 203. The refrigerant flowing out of the heat exchanger 203 is sucked into the compressor 201 again.

Although FIG. 1 shows an example in which the flow of the refrigerant is in a fixed direction in the refrigerant circuit A1, a flow path switching device is provided on the discharge side of the compressor 201 so that the flow of the refrigerant can be reversed. You may. When the flow path switching device is provided, the heat exchanger 100 also functions as an evaporator, and the heat exchanger 203 also functions as a condenser. As the flow path switching device, for example, a combination of two-way valves, a combination of three-way valves, or a four-way valve can be adopted.

Further, carbon dioxide is desirable as the refrigerant used in the refrigeration cycle apparatus 200, but the use is not limited to carbon dioxide. In addition to carbon dioxide, natural refrigerants such as hydrocarbons or helium, chlorine-free alternative refrigerants such as HFC410A, HFC407C or HFC404A, or chlorofluorocarbon refrigerants used in existing products such as R22 or R134a are also used. It is possible.

<Detailed configuration of heat exchanger 100>
FIG. 3 is an explanatory diagram for explaining an example of forming a protrusion of the first pipe. FIG. 4 is an explanatory diagram for explaining an example of forming a protrusion of a conventional first pipe as a comparative example. Based on FIG. 3, the first pipe will be described in detail in comparison with the first pipe of FIG. In addition, in the conventional example of FIG. 4, "X" is added to the end of the code to distinguish it from the first pipe 1. For convenience, a case where two protrusions are formed on the first pipe by using two jigs will be described. Further, in FIGS. 3 and 4, (a) schematically shows a state in which the first pipe is viewed from the side surface, and (b) schematically shows a state in which the first pipe is projected in the pipe axis direction. ing. Further, in FIGS. 3 and 4, the pipe shaft is shown as the pipe shaft CL.

As shown in FIG. 3, when forming the two protrusions 3 on the first pipe 1, a plurality of gear-shaped jigs are used. One of the gear-shaped jigs is referred to as a jig 6a, and the other is referred to as a jig 6b. Further, the protrusion 3 formed by the jig 6a is referred to as a protrusion 3a, and the protrusion 3 formed by the jig 6b is referred to as a protrusion 3b. In the state shown in FIG. 3, a protrusion 3a formed by the jig 6a is installed on the upstream side of the flow of the first heat medium, and is formed by the jig 6b on the downstream side of the flow of the first heat medium. It is assumed that the protrusion 3b is installed.

The jig 6a has a gear 9A. A plurality of convex portions 9a for forming the protrusions 3a are formed on the gear 9A so as to have different intervals. When the outer surface of the first pipe 1 is pressed by the jig 6a, the inner surface of the first pipe 1 is projected by the convex portion 9a of the gear 9A, and a plurality of protrusions 3a are formed as stripes in the spiral direction. The intervals between the plurality of protrusions 3a formed by the jig 6a are shown as pitch 5a, pitch 5b, and pitch 5c.

Similarly, the jig 6b has a gear 9B. A plurality of convex portions 9b for forming the protrusions 3b are formed on the gear 9B so as to have different intervals. When the outer surface of the first pipe 1 is pressed by the jig 6b, the inner surface of the first pipe 1 is projected by the convex portion 9b of the gear 9B, and a plurality of protrusions 3b are formed as other stripes in the spiral direction. The intervals between the plurality of protrusions 3b formed by the jig 6b are shown as pitch 5d, pitch 5e, and pitch 5f.

As shown in FIG. 3, the pitch 5a, the pitch 5b, and the pitch 5c of the protrusions 3a have different lengths. That is, the plurality of protrusions 3a are formed at unequal intervals.
Similarly, the pitch 5d, the pitch 5e, and the pitch 5f of the protrusions 3b have different lengths. That is, the plurality of protrusions 3b are formed at unequal intervals.
Here, the unequal spacing refers to a case where two or more lengths of spacing between the jigs 6a and the protrusions 3 formed by the jigs 6b exist.

The positional relationship between the protrusions 3a and the protrusions 3b is determined by the phase difference between the gear 9A of the jig 6a and the gear 9B of the jig 6b. That is, in the jig 6a, since the intervals of the plurality of convex portions 9a are formed at unequal intervals, the plurality of protrusions 3a formed are also formed at unequal intervals. Similarly, in the jig 6b, since the intervals of the plurality of convex portions 9b are formed at unequal intervals, the plurality of protrusions 3b formed are also formed at unequal intervals. Therefore, the flow of the first heat medium is agitated in both the protrusions 3a and 3b, and the heat exchange performance is improved.

On the other hand, in the conventional example of FIG. 4, when forming the two protrusions 3X on the first pipe 1X, the jig 6aX and the jig 6bX are used, but the distance between the convex portions 9aX of the gear 9AX of the jig 6aX , And the distance between the convex portions 9bX of the gear 9BX of the jig 6bX is constant. Further, as shown in FIG. 4, the distance between the protrusion 3aX and the protrusion 3bX adjacent to each other in the pipe axis direction is equal. Therefore, as shown in FIG. 4, the pitch 5aX, the pitch 5bX, and the pitch 5cX of the protrusions 3aX have the same length. That is, the plurality of protrusions 3aX are formed at equal intervals. Similarly, the pitch 5dX, the pitch 5eX, and the pitch 5fX of the protrusions 3bX have the same length. That is, the plurality of protrusions 3bX are formed at equal intervals.

That is, in the jig 6aX, since the intervals of the plurality of convex portions 9aX are formed at equal intervals, the plurality of protrusions 3aX formed are also formed at equal intervals. Similarly, in the jig 6bX, since the intervals of the plurality of convex portions 9bX are formed at equal intervals, the plurality of protrusions 3bX formed are also formed at equal intervals. Therefore, the protrusions 3aX and the protrusions 3bX are all installed side by side in the pipe axis direction. In this case, the effect of improving the heat exchange performance by the protrusion 3bX installed on the downstream side is reduced. This is because the protrusion 3aX agitates the flow of the first heat medium and improves the heat exchange performance, but the protrusion 3bX reduces the flow velocity and the stirring effect of the flow of the first heat medium. is there.

<Manufacturing method of the first pipe 1>
The manufacturing method of the first pipe 1 will be described with reference to FIG. 3 in comparison with the conventional example of FIG. Here, for convenience, a case where two protrusions are formed on the first pipe by using two jigs will be described.

As a method of forming a plurality of protrusions 3 on the inner surface of the first pipe 1, as shown in FIG. 3, a jig 6a having a gear 9A and a jig 6B having a gear 9B are used. A plurality of convex portions 9a are formed on the gear 9A. A plurality of convex portions 9b are formed on the gear 9B. Then, the convex portion 9a is pressed against the outer wall of the first pipe 1 to form one spiral protrusion 3a on the inner surface of the first pipe 1. Similarly, the convex portion 9b is pressed against the outer wall of the first pipe 1 to form one spiral protrusion 3b on the inner surface of the first pipe 1. That is, two spirally formed protrusions 3 are formed on the first pipe 1.

The jig 6a and the jig 6b are rotated independently, and the convex portions 9a and the convex portions 9b formed intermittently are pressed against the outer surface of the first pipe 1 one after another. By doing so, the two protrusions 3 are spirally formed on the first pipe 1. Since the spacing between the convex portions 9a and the spacing between the convex portions 9b are unequal, the protrusions 3a formed by the convex portions 9a and the protrusions 3b formed by the convex portions 9b are also unequally spaced. Become.

On the other hand, in the conventional example shown in FIG. 4, by rotating the jig 6aX and the jig 6bX, respectively, two protrusions 3X are spirally formed in the first pipe 1X, but each convex portion 9aX And the interval of each convex portion 9bX are constant intervals, that is, equal intervals. Therefore, the protrusions 3aX formed by the convex portions 9aX and the protrusions 3bX formed by the convex portions 9bX are also at regular intervals, that is, at equal intervals.

FIG. 5 is an explanatory diagram for explaining the first pipe 1 provided with the protrusion 3 formed by the method of FIG. FIG. 6 is an explanatory diagram for explaining the first pipe 1X provided with the protrusion 3X formed by the method of FIG. Based on FIG. 5, the first pipe will be described in detail in comparison with the first pipe of FIG. Note that, in FIGS. 5 and 6, (a) schematically shows a state in which the first pipe is viewed from the side surface, and (b) schematically shows a state in which the first pipe is projected in the pipe axis direction. ing. Further, in FIGS. 5 and 6, the pipe shaft is shown as the pipe shaft CL.

As shown in FIG. 5, protrusions 3a are formed at unequal intervals in the first pipe 1. That is, the pitch 5a, the pitch 5b, and the pitch 5c of the protrusions 3a have different lengths.
Similarly, protrusions 3b are formed at unequal intervals in the first pipe 1. That is, the pitch 5d, the pitch 5e, and the pitch 5f of the protrusion 3a have different lengths.
Therefore, even if the distance between the protrusions 3a and 3b is equal, the protrusions 3a and 3b adjacent to each other in the pipe axis direction do not line up in the pipe axis direction.

As shown in FIG. 5, the protrusion 3a-1 on the uppermost stage of the paper surface is formed on the straight line La1, the second protrusion 3a-2 from the paper surface is formed on the straight line La2, and the third protrusion 3a-from the paper surface. Reference numeral 3 is formed on the straight line La3, and the protrusion 3a-4 at the bottom of the paper surface is formed on the straight line La4.
The straight lines La1 to La4 are straight lines parallel to the tube axis CL, respectively. In the following description, the straight lines La1 to La4 may be collectively referred to as a straight line La. The fact that the protrusion 3a is formed on the straight line La parallel to the tube axis CL means that the portion including the apex of the protrusion 3a overlaps the straight line La.

Similarly, the protrusion 3b-1 on the uppermost stage of the paper surface is formed on the straight line Lb1, the second protrusion 3b-2 from the paper surface is formed on the straight line Lab, and the third protrusion 3b-3 from the paper surface is the straight line Lb3. The protrusions 3b-4 at the bottom of the paper surface are formed on the straight line Lb4.
The straight lines Lb1 to Lb4 are straight lines parallel to the tube axis CL, respectively. In the following description, the straight lines Lb1 to Lb4 may be collectively referred to as a straight line Lb. The fact that the protrusion 3b is formed on the straight line Lb parallel to the tube axis CL means that the portion including the apex of the protrusion 3b overlaps the straight line Lb.

That is, the protrusions 3a-1 and the protrusions 3b-1 are formed on different straight lines parallel to the pipe axis CL, and are not overlapped and arranged in the pipe axis direction. Similarly, the protrusions 3a-2 and the protrusions 3b-2 Is formed on different straight lines parallel to the pipe axis CL, and does not overlap and line up in the pipe axis direction. Similarly, the protrusions 3a-3 and the protrusions 3b-3 are formed on different straight lines parallel to the pipe axis CL, and do not overlap and line up in the pipe axis direction. Similarly, the protrusions 3a-4 and the protrusions 3b-4 are formed on different straight lines parallel to the pipe axis CL, and do not overlap and line up in the pipe axis direction.

Therefore, even in the protrusions 3b formed on the downstream side of the flow of the first heat medium, the flow velocity does not decrease, and the stirring effect of the flow of the first heat medium does not decrease. Therefore, the flow of the first heat medium is agitated at both the protrusions 3a and 3b, and the effect of improving the heat exchange performance is not reduced.

On the other hand, in the conventional example of FIG. 6, protrusions 3aX are formed at regular intervals on the first pipe 1X. That is, the pitch 5aX, the pitch 5bX, and the pitch 5cX of the protrusions 3aX have the same length, respectively.
Similarly, protrusions 3bX are formed at regular intervals in the first pipe 1X. That is, the pitch 5dX, the pitch 5eX, and the pitch 5fX of the protrusions 3aX have the same length, respectively.
Therefore, when the distances between the protrusions 3aX and the protrusions 3bX are equal, the protrusions 3aX and the protrusions 3bX adjacent to each other in the pipe axis direction are aligned in the pipe axis direction with a certain phase difference.

As shown in FIG. 6, the protrusions 3a-5X at the bottom of the paper surface are formed on the straight line La5.
The straight line La5 is a straight line parallel to the pipe axis CL, similarly to the straight lines La1 to La4. The fact that the protrusion 3aX is formed on the straight line La parallel to the tube axis CL means that the portion including the apex of the protrusion 3aX overlaps the straight line La. Further, the protrusions 3a-4X are formed fourth from the paper surface in FIG.

Similarly, the protrusions 3b-5X4 at the bottom of the paper surface are formed on the straight line Lb4.
The straight line Lb5 is a straight line parallel to the tube axis CL, similarly to the straight lines Lb1 to Lb4. The fact that the protrusion 3bX is formed on the straight line Lb parallel to the tube axis CL means that the portion including the apex of the protrusion 3bX overlaps the straight line Lb. Further, the protrusions 3b-4X are formed fourth from the paper surface in FIG.

Here, as shown in FIG. 6, in the side view state, the straight line La1 and the straight line Lb1 overlap in the pipe axis direction and are the same straight line. Similarly, the straight line La2 and the straight line Lb2 overlap in the pipe axis direction and are the same straight line. Similarly, the straight line La3 and the straight line Lb3 overlap in the pipe axis direction and are the same straight line. Similarly, the straight line La4 and the straight line Lb4 overlap in the pipe axis direction and are the same straight line. Similarly, the straight line La5 and the straight line Lb5 overlap in the pipe axis direction and are the same straight line.

That is, the protrusions 3a-1X and the protrusions 3b-1X are formed on the same straight line parallel to the pipe axis CL, and are arranged so as to overlap in the pipe axis direction. Similarly, the protrusions 3a-2X and the protrusions 3b-2X are formed on the same straight line parallel to the pipe axis CL, and are arranged so as to overlap in the pipe axis direction. Similarly, the protrusions 3a-3X and the protrusions 3b-3X are formed on the same straight line parallel to the pipe axis CL, and are arranged so as to overlap in the pipe axis direction. Similarly, the protrusions 3a-4X and the protrusions 3b-4X are formed on the same straight line parallel to the pipe axis CL, and are arranged so as to overlap in the pipe axis direction. Similarly, the protrusions 3a-5X and the protrusions 3b-5X are formed on the same straight line parallel to the pipe axis CL, and are arranged so as to overlap in the pipe axis direction.

Therefore, as shown by the arrow F in FIG. 6, the protrusion 3aX formed on the upstream side of the flow of the first heat medium agitates the flow of the first heat medium, but on the downstream side of the flow of the first heat medium. In the formed protrusions 3bX, the flow velocity becomes small, and the stirring effect of the flow of the first heat medium becomes small. That is, the effect of improving the heat exchange performance by the protrusions 3bX formed on the downstream side of the flow of the first heat medium is reduced.

<Modification example of the first pipe 1>
FIG. 7 is an explanatory diagram for explaining another example of forming the protrusion of the first pipe. The effect of the heat exchanger 100 provided with the first pipe 1 will be described with reference to FIG. 7. In FIG. 7, (a) schematically shows a state in which the first pipe is viewed from the side surface, and (b) schematically shows a state in which the first pipe is projected in the pipe axis direction. Further, here, for convenience, a case where two protrusions are formed on the first pipe by using two jigs will be described.

In FIG. 7, similarly to FIG. 3, when a plurality of protrusions 3 are formed in a spiral shape, the distance between the protrusions 3a and the distance between the protrusions 3b provided by the same jig 6a and the jig 6b are different 2 The case where they are formed at unequal intervals having a length of more than one kind is shown schematically. Although the jig 6a and the jig 6b have the same configuration, the distance between the convex portions 9a and the distance between the convex portions 9b are different lengths.

As shown in FIG. 7, when the intervals between the convex portions 9a and the intervals between the convex portions 9b are unequal intervals, the protrusions 3a and 3b are also formed in the first pipe 1 at unequal intervals. Further, although the distance between the convex portions 9a and the distance between the convex portions 9b are different, some protrusions 3a and 3b adjacent to each other in the pipe axis direction may be aligned in the pipe axis direction. Consider this case. Note that FIG. 7 shows an example in which the protrusion 3a-1 on the uppermost stage of the paper surface and the protrusion 3b-1 on the uppermost stage of the paper surface are arranged in the pipe axis direction.

Also in FIG. 7, the intervals between the convex portions 9a and the intervals between the convex portions 9b are unequal intervals, and the intervals between the convex portions 9a and the convex portions 9b are different between the jig 6a and the jig 6b. Therefore, the protrusions 3 other than the uppermost protrusion 3a-1 and the uppermost protrusion 3b-1 are not aligned in the pipe axis direction. Therefore, even if some of the protrusions 3 are lined up in the pipe axis direction, deterioration of the heat exchange performance can be suppressed and the heat exchange performance can be improved as compared with the first pipe which is a conventional example.

<Detailed configuration of jig 6a and jig 6b>
8 and 9 are explanatory views for explaining the distance between the protrusions 3 of the first pipe 1. Based on FIGS. 8 and 9, in order to realize the unequal spacing of the protrusions 3, the jigs having the same configuration, that is, the maximum distance between the protrusions 3a and 3b formed by the jigs 6a and 6b, respectively. The angle and the minimum angle will be described. 8 and 9, FIG. 8A schematically shows a state in which the first pipe is viewed from the side surface, and FIG. 9B schematically shows a state in which the first pipe is projected in the pipe axis direction. ing. Further, the angle θ between the protrusions 3a is formed by two straight lines connecting the center of the first pipe 1 and the center of the target protrusion 3a.

First, the minimum value of the angle of the interval between the protrusions 3a given to the first pipe 1 by the jig 6a, that is, the minimum angle θ1 [rad] will be described with reference to FIG.
FIG. 8 shows an example in which five protrusions 3a are formed from the upper part of the paper surface to the lower part of the paper surface, and the protrusions 3a-1, the protrusions 3a-2, the protrusions 3a-3, and the protrusions 3a are shown from the upper side of the paper surface. -4, shown as protrusions 3a-5. It is assumed that the protrusions 3a-1, the protrusions 3a-2, the protrusions 3a-3, the protrusions 3a-4, and the protrusions 3a-5 are formed in the same shape and size.

Here, as shown in FIG. 8B, the width of the protrusion 3a, that is, the diameter of the protrusion 3a is defined as the width W. Further, as shown in FIG. 8B, the length corresponding to the width W of the protrusion 3a is defined as the length 3b1. Further, the inner diameter of the first pipe 1 is defined as the inner diameter Dwi.

Consider a case where the protrusion 3b is provided by the jig 6b between the protrusion 3a-1 provided by the jig 6a and the protrusion 3a-2 provided by the jig 6a next. In FIG. 8B, when the protrusion 3a provided by the jig 6a and the protrusion 3b provided by the jig 6b are not overlapped with each other, between the protrusions 3a-1 and the protrusions 3a-2. The minimum angle θ1 can be obtained by the equation (1).

Next, the maximum value of the angle of the interval between the protrusions 3a provided to the first pipe 1 by the jig 6a based on FIG. 9, that is, the maximum angle θ2 [rad] will be described. It should be noted that the first pipe 1 will be described as forming n protrusions 3 per circumference.
FIG. 9 shows an example in which four protrusions 3a are formed from the upper part of the paper surface to the lower part of the paper surface, and the protrusions 3a-1, the protrusions 3a-2, the protrusions 3a-3, and the protrusions 3a are shown from the upper side of the paper surface. It is shown as -4. It is assumed that the protrusions 3a-1, the protrusions 3a-2, the protrusions 3a-3, and the protrusions 3a-4 are formed in the same shape and size.

The distance from the protrusion 3a-1 to the protrusion 3a-2 is determined by the above-mentioned minimum angle θ1. Further, the angle from the protrusion 3a-2 to the protrusion 3a-3 does not overlap from the protrusion 3a-1 to the protrusion 3a-2 and is made unequal, so that the angle is θ1 × 3/2, that is, 1.5 of θ1. Double. Similarly, the angle from the protrusion 3a-3 to the protrusion 3a-4 is θ1 × 4/2. Therefore, the angle from the protrusion 3a-1 to the protrusion 3a-4 is θ1 × 9/2.

Therefore, the angle corresponding to the maximum angle θ2'[rad], which is the maximum interval when the protrusions 3a are four, can be obtained by the equation (2).

In the formula (2), the maximum angle θ2 when the number of protrusions 3 installed is n (n> 2) can be expressed by the formula (3).

From the above, the angle between the protrusions 3 provided by the jig 6a is within the range of the equation (4).

Here, the relationship between the adjacent protrusions 3a and 3b has been described by taking as an example the case where the protrusions 3 are formed by two jigs, that is, the jigs 6a and 6b. That is, the above description applies to the relationship of protrusions formed so as to be adjacent to each other in each jig when the protrusions are formed by using a plurality of jigs. However, although the case where the protrusion 3 is formed by two jigs is given as an example, the number of jigs is not particularly limited. Even when there are two or more jigs, the range of angles between the protrusions 3 can be obtained by the equation (4). In this way, if the distances between the protrusions 3 provided by the same jig are unequal, the effect of improving the heat exchange performance can be obtained.

[Effects of the heat exchanger 100, the refrigeration cycle device 200, and the manufacturing method of the heat exchanger]
As described above, in the heat exchanger 100, one protrusion 3a and the protrusion 3b adjacent to the protrusion 3a are formed on different straight lines parallel to the pipe axis direction, and the first pipe 1 is piped. Adjacent protrusions 3 do not overlap when projected in the axial direction. Therefore, according to the heat exchanger 100, the phenomenon described in FIG. 6 is unlikely to occur, and the heat exchange performance is improved.

According to the heat exchanger 100, since the protrusions 3 formed in one strip are arranged at unequal intervals, the adjacent protrusions 3 are projected in the pipe axis direction when the first pipe 1 is projected. It can be prevented from overlapping.

According to the heat exchanger 100, since the angle θ between the protrusions 3 is configured to be within the range of the above equation (4), the first pipe 1 is adjacent in a state of being projected in the pipe axis direction. The protrusions 3 can be prevented from overlapping.

According to the refrigeration cycle apparatus 200, since the above heat exchanger is provided as a condenser, improvement in heat exchange performance in the condenser can be expected.

In the method of manufacturing the heat exchanger 100, the protrusions 3a are formed at unequal intervals by arranging the plurality of protrusions 9a of the jig 6a at unequal intervals, and the plurality of protrusions of the jig 6b are formed at unequal intervals. By arranging each of the portions 9b at unequal intervals, each of the protrusions 3b is formed at unequal intervals. Therefore, according to the method for manufacturing the heat exchanger 100, it is possible to manufacture the heat exchanger 100 without going through a special jig and a special process.

Embodiment 2.
FIG. 10 is an explanatory diagram for explaining the shape of the first pipe 1A of the heat exchanger according to the second embodiment of the present invention. The shape of the first pipe 1A of the heat exchanger according to the second embodiment will be described with reference to FIG.
In the second embodiment, the differences from the first embodiment will be mainly described, and the same parts as those in the first embodiment are designated by the same reference numerals and the description thereof will be omitted. Further, in FIG. 10, (a) schematically shows a state in which the first pipe is viewed from the side surface, and (b) schematically shows a state in which the first pipe is projected in the pipe axis direction.

In the first embodiment, the case where the first pipe 1 is a circular pipe having no unevenness on the outer peripheral surface is shown as an example, but in the second embodiment, the first pipe 1A has one line on the outer peripheral surface. The case where the corrugated pipe is formed with the spiral groove 35 will be described as an example. When the protrusion 3 is formed in the first pipe 1A, it is formed in a portion other than the spiral groove 35 as shown in FIG. The second pipe is wound around the spiral groove 35 of the first pipe 1B.

By forming the first pipe 1A with a corrugated pipe in this way, it becomes possible to further promote the turbulent flow of the refrigerant inside the first pipe 1A. Therefore, the heat exchange performance can be further improved as compared with the case where the first pipe 1 described in the first embodiment is provided with the protrusion.

Embodiment 3.
FIG. 11 is an explanatory diagram for explaining the shape of the first pipe 1B of the heat exchanger according to the third embodiment of the present invention. The shape of the first pipe 1B of the heat exchanger according to the second embodiment will be described with reference to FIG.
In the third embodiment, the differences from the first embodiment will be mainly described, and the same parts as those in the first embodiment are designated by the same reference numerals and the description thereof will be omitted. Further, in FIG. 11, (a) schematically shows a state in which the first pipe is viewed from the side surface, and (b) schematically shows a state in which the first pipe is projected in the pipe axis direction.

In the first embodiment, the case where the first pipe 1 is a circular pipe having no unevenness on the outer peripheral surface is shown as an example, but in the third embodiment, the first pipe 1B has a peak portion 30a and a valley. The case of a twisted pipe having a portion 30b will be described as an example. The mountain portion 30a is a portion protruding in the diameter-expanding direction in which the diameter of the first pipe 1B expands, and is spirally formed in the direction in which the first heat medium of the first flow path FP1 flows. The valley portion 30b has an outer diameter smaller than the portion where the mountain portion 30a is formed, and is a portion around which the second pipe is wound, and is formed spirally along the mountain portion 30a. When the protrusion 3 is formed on the first pipe 1B, it is formed on the valley portion 30b as shown in FIG. That is, the protrusion 3 is formed in the spiral direction, which is the formation direction of the valley portion 30b. The second pipe is wound around the first pipe 1B so as to be fitted in the valley portion 30b.

By forming the first pipe 1B with a twisted pipe in this way, it is possible to further promote the turbulent flow of the refrigerant inside the first pipe 1B. Further, the contact area between the first pipe 1B and the second pipe can be increased. Therefore, the heat exchange performance can be further improved as compared with the case where the first pipe 1 described in the first embodiment is provided with the protrusion.

Although the present invention has been described by dividing the embodiment, the specific configuration is not limited to the described embodiment and can be changed without departing from the gist of the invention.

1 1st pipe, 1A 1st pipe, 1B 1st pipe, 1X 1st pipe, 1a inlet, 1b outlet, 2nd pipe, 2a inlet, 2b outlet, 3 protrusions, 3X Protrusions, 3a protrusions, 3a-1 protrusions, 3a-1X protrusions, 3a-2 protrusions, 3a-2X protrusions, 3a-3 protrusions, 3a-3X protrusions, 3a-4 protrusions, 3a-4X protrusions, 3a-5 protrusions, 3a-5X protrusion, 3aX protrusion, 3b protrusion, 3b-1 protrusion, 3b-1X protrusion, 3b-2 protrusion, 3b-2X protrusion, 3b-3 protrusion, 3b-3X protrusion, 3b-4 protrusion, 3b-4X protrusion , 3b-5X protrusion, 3b-5X4 protrusion, 3bX protrusion, 5a pitch, 5aX pitch, 5b pitch, 5bX pitch, 5c pitch, 5cX pitch, 5d pitch, 5dX pitch, 5e pitch, 5eX pitch, 5f pitch, 5fX pitch, 6B jig, 6a jig, 6aX jig, 6b jig, 6bX jig, 9A gear, 9AX gear, 9B gear, 9BX gear, 9a convex part, 9aX convex part, 9b convex part, 9bX convex part, 10A heat Medium piping, 20A refrigerant piping, 30a peaks, 30b valleys, 35 spiral grooves, 60 control devices, 100 heat exchangers, 200 refrigeration cycle devices, 201 compressors, 202 throttle devices, 203 heat exchangers, 203A blowers, 205 Pump, 207 Hot water storage tank, A1 Refrigerant circuit, A2 Heat medium circuit, A3 Water supply circuit, FP1 1st flow path, FP2 2nd flow path, U Hot water supply utilization unit.

Claims (7)

The first pipe through which the first heat medium flows and
The second pipe around which the second heat medium flows, which is wound around the first pipe,
Have,
The first pipe
It has a plurality of protrusions protruding on the inner surface,
The protrusion
A plurality of the first pipes are spirally formed in the direction in which the first heat medium flows.
A heat exchanger in which each of the protrusions formed in one strip is arranged at irregular intervals. Of the protrusions formed on one strip and the protrusions formed on the other strip, two adjacent protrusions in the pipe axis direction of the first pipe are different straight lines parallel to the pipe axis direction. The heat exchanger according to claim 1, which is formed above. In a state where the first pipe is projected in the pipe axis direction,
Let the width of the protrusion be W
The inner diameter of the first pipe is Dwi.
When the number of the protrusions formed per circumference of the first pipe is n.
The angle θ between the protrusions is

The heat exchanger according to claim 1 or 2, which is configured to be in the range of. The heat exchanger according to any one of claims 1 to 3, wherein the first pipe is a corrugated pipe. The first pipe
A mountain portion protruding in the diameter expansion direction in which the diameter of the first pipe expands,
The outer diameter is smaller than the portion where the mountain portion is formed, and the valley portion around which the second pipe is wound is included.
The mountain part
It is formed spirally in the direction in which the first heat medium of the first flow path flows.
The valley is
Formed spirally along the mountain,
The heat exchanger according to any one of claims 1 to 3, wherein the protrusion is formed in a spiral direction which is a formation direction of the valley portion. The heat exchanger according to any one of claims 1 to 5 is provided as a condenser.
In the heat exchanger
The first heat medium flowing through the first flow path of the first pipe constituting the heat exchanger is
A refrigeration cycle device that is heated by a second heat medium that flows through a second flow path of a second pipe that constitutes the heat exchanger. The first pipe in which the first flow path through which the first heat medium flows is formed, and
A second flow path through which the second heat medium flows is formed, and has a second pipe wound around the first pipe.
The outer surface of the first pipe is pressed by using a plurality of jigs having gears having a plurality of convex portions formed therein, and the plurality of protrusions protruding from the inner surface of the first pipe are spirally formed. It is a method of manufacturing a heat exchanger that forms multiple rows.
A method for manufacturing a heat exchanger in which each of the plurality of protrusions is arranged on the gear at unequal intervals in each of the jigs, and each of the protrusions is formed at unequal intervals.

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