JP2003322432A - Heat exchanger and air conditioner - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger easily usable for comfortable air conditioning for reducing nonuniformity of the temperature distribution after air passes through the heat exchanger by reducing the ratio of the area of a overheat gas area to the heat exchange area of a refrigerant pipe. <P>SOLUTION: This heat exchanger has an introducing side tank part 101, a discharge side tank part 102, and the refrigerant pipe 103 arranged between introducing side-discharge side two tank parts, and connecting both, and vaporizes a refrigerant by exchanging heat between an external fluid and the refrigerant flowing in the refrigerant pipe 103 in a process of introducing and discharging the refrigerant introduced to the introducing side tank part 101 to the discharge side tank part 102 via the refrigerant pipe 103, and is characterized by arranging a first regulating part in the refrigerant pipe 103 for regulating the flowing direction of the vaporized refrigerant so as to become almost parallel to the flowing direction of the external fluid. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchanger and an air conditioner provided with the heat exchanger, and more particularly to a heat exchanger as an evaporator.

[0002]

2. Description of the Related Art Conventionally, as this type of heat exchanger, a heat exchanger 10 shown in FIG. 8 is known as being used in an air conditioner for a vehicle. The heat exchanger 10 shown in FIG. 8 includes an introduction side tank section 11 and a discharge side tank section 12
And a plurality of refrigerant pipes 13 that connect the introduction-side tank portion 11 and the discharge-side tank portion 12. Also,
An external fluid that exchanges heat with the refrigerant is configured to pass through the outside of the refrigerant pipe 13 in a direction substantially orthogonal to the longitudinal direction of the refrigerant pipe 13.

In the heat exchanger 10 having the above structure, the liquid refrigerant flows from the introduction side tank portion 11 and flows through the refrigerant pipe 13 from the lower side to the upper side. When flowing through the refrigerant pipe 13, the liquid refrigerant absorbs the heat of the air by heat exchange with the air (external fluid), and evaporates and vaporizes. The vaporized refrigerant passes through the discharge side tank portion 12 and flows out from the heat exchanger 10.

In the mixed region of the liquid refrigerant and the vaporized refrigerant in the refrigerant pipe 13, the heat absorbed from the external fluid is used for vaporizing the liquid refrigerant, and the temperatures of the liquid refrigerant and the vaporized refrigerant are kept constant. Be done. In the region containing only the vaporized refrigerant (superheated gas region), the heat absorbed from the external fluid is used to raise the temperature of the vaporized refrigerant.
The external fluid passing through the mixed region of the liquid refrigerant and the vaporized refrigerant is cooled to a predetermined temperature by heat exchange because the temperature of the refrigerant is kept constant, but the external fluid passing through the superheated gas region is the refrigerant. Since the temperature is rising, the heat is not sufficiently exchanged and is not cooled to a predetermined temperature, that is, it flows out while the temperature remains high.

[0005]

By the way, in the conventional heat exchanger, the ratio of the area of the superheated gas region to the heat exchange area of the refrigerant pipe is large, and therefore the ratio of the air having a high temperature passing through the superheated gas region. There was a problem that it was difficult to use for comfortable air conditioning because the temperature was high and the temperature distribution became uneven.

The present invention has been made in consideration of such circumstances, and an object thereof is to provide a heat exchanger having a small temperature distribution unevenness and easy to use for comfortable air conditioning.

[0007]

According to the heat exchanger of the present invention,
In order to solve the above problems, the following means were adopted. The invention according to claim 1 includes an introduction-side tank portion, a discharge-side tank portion, and a refrigerant pipe that is arranged between the two tank portions on the introduction side and the discharge side to connect the two, and the introduction-side tank portion In the process of introducing the refrigerant introduced into the refrigerant tank to the discharge side tank portion through the refrigerant pipe and discharging it, an external fluid is caused to flow so as to come into contact with the outer surface of the refrigerant pipe in a direction substantially orthogonal to the longitudinal direction of the refrigerant pipe. In a heat exchanger in which heat is exchanged between the fluid and the refrigerant flowing through the refrigerant pipe, the refrigerant is evaporated and vaporized,
It is characterized in that the refrigerant pipe is provided with a first restricting portion for restricting the flow direction of the vaporized refrigerant so as to be substantially parallel to the flow direction of the external fluid.

According to the heat exchanger of the present invention, since the direction of the flow of the overheated vaporized refrigerant is parallel to the external fluid due to the first restricting portion, it can be seen from the upstream side or the downstream side of the external fluid. At this time, the ratio of the area of the superheated gas area to the heat exchange area of the refrigerant pipe becomes small. Therefore, the ratio of the external fluid passing through the superheated gas region is reduced, and the temperature unevenness of the external fluid passing through the heat exchanger is reduced.

According to a second aspect of the present invention, in the heat exchanger according to the first aspect, a heat exchange area enlarging means for enlarging a heat exchange area between the external fluid and the refrigerant is provided inside the refrigerant pipe. Is characterized by.

According to the heat exchanger of the present invention, the area of the heat exchange surface between the external fluid and the refrigerant is expanded by the heat exchange area expanding means provided inside the refrigerant pipe, and the heat in the same time is reduced. The amount of heat exchange can be increased, or the same amount of heat can be exchanged in a shorter time. This makes it possible to compensate for heat exchange in a region having a poor heat exchange capacity (for example, a superheated gas region), so that temperature unevenness of the external fluid passing through the heat exchanger is reduced.

According to a third aspect of the present invention, in the heat exchanger according to the first aspect, the refrigerant pipe is provided with a refrigerant flow disturbing means configured to disturb the flow of the refrigerant inside the refrigerant pipe. Characterize.

According to the heat exchanger of the present invention, the refrigerant flow disturbing means disturbs the refrigerant flow in the refrigerant pipe, promotes heat transfer inside the refrigerant flow, and increases the amount of heat exchange within the same time. Or the same amount of heat can be exchanged in a shorter time. This makes it possible to compensate for heat exchange in a region having a poor heat exchange capacity, for example, in a superheated gas region, so that temperature unevenness of the external fluid passing through the heat exchanger is reduced.

According to a fourth aspect of the present invention, in the heat exchanger according to the first aspect, the refrigerant pipe is provided substantially at the center in the longitudinal direction.
It is characterized in that a second restricting portion that causes the flow of the refrigerant to meander is provided.

According to the heat exchanger of the present invention, the flow of the refrigerant meanders in the refrigerant pipe due to the second restriction portion, and the refrigerant is biased to the upstream side or the downstream side of the external fluid in the refrigerant pipe. Therefore, it is possible to prevent the area of the superheated gas region from expanding, and therefore, the temperature unevenness of the external fluid passing through the heat exchanger is reduced.

The invention according to claim 5 is based on claims 1 to 4.
In the heat exchanger described in any one of the above 1, the introduction side tank portion, the discharge side tank portion, and the refrigerant pipe are configured as two divided bodies of the same shape which are divided into two in the longitudinal direction of the refrigerant pipe.

According to the heat exchanger of the present invention, the introduction side tank portion, the discharge side tank portion and the refrigerant pipe are formed as two divided bodies having the same shape, so that the number of assembling steps can be reduced. Also, since there is only one type of parts,
For example, capital investment costs at the time of production, such as press forming die costs, can be suppressed, and the cost reduction effect can be increased.

According to a sixth aspect of the present invention, in the heat exchanger according to the fifth aspect, the two divided bodies are expanded, some of them are joined together to be integrally formed, and the joined portion is bent into two pieces. Characterized by overlapping the body.

According to the heat exchanger of the present invention, the introduction side tank portion, the discharge side tank portion and the refrigerant pipe are integrally formed by connecting a part of the two divided bodies, and the connected portion is bent. Since they are configured by stacking them together, the assembly process can be reduced. Since the number of types of parts is one, for example, the capital investment cost at the time of production such as the press forming die cost can be suppressed, and the cost reduction effect becomes large.

According to a seventh aspect of the present invention, in the heat exchanger according to the first aspect, the introduction side tank portion and the discharge side tank portion are formed of hollow bodies, and the refrigerant pipe is divided into two parts in the longitudinal direction of the refrigerant pipe. It is characterized in that it is configured as two pipe division bodies of the same shape.

According to the heat exchanger of the present invention, since the introduction side tank section and the discharge side tank section are composed of hollow bodies, it is easy to secure the wall thickness of the introduction side tank section and the discharge side tank section. . Further, since the two tank parts on the introduction side and the discharge side are separate parts in the formation of the two pipe divisions, for example, the step of forming the two tank parts on the introduction side and the discharge side such as deep drawing becomes unnecessary. , Easy to manufacture.

The invention according to claim 8 relates to claims 1 to 7.
An air conditioner comprising the heat exchanger according to any one of 1.

According to the air conditioner of the present invention,
The area of the superheated gas area is small relative to the heat exchange area of the refrigerant pipe of the heat exchanger, the ratio of the external fluid passing through the superheated gas area can be reduced, and the temperature unevenness of the external fluid passing through the heat exchanger is reduced. .

[0023]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is an exploded perspective view of a first embodiment of a heat exchanger according to the present invention. In FIG. 1, the heat exchanger 100 is composed of an introduction side tank section 101, a discharge side tank section 102, and a plurality of refrigerant pipes 103 connecting the introduction side tank section 101 and the discharge side tank section 102, and A plurality of heat exchange segments 110 in which the introduction side tank portion 101, the discharge side tank portion 102, and the refrigerant pipe 103 are formed are connected and laminated. The heat exchange segment 110 is configured by stacking press-formed divided bodies 111 and 112, and the introduction-side tank portion 101 includes the heat exchange segment 11
0, the discharge side tank portion 102 is formed above the heat exchange segment 110, and the refrigerant pipe 103
Is formed between the introduction side tank portion 101 and the discharge side tank portion 102. Further, the first wall portion (first regulation portion) 11 is provided between the discharge side tank portion 102 and the refrigerant pipe 103.
3 is a direction substantially orthogonal to the longitudinal direction of the divided body 111, and when the divided bodies 111 and 112 are superposed, the refrigerant pipe 103
The first opening 114 is provided on the downstream side of the first wall 113 in the air. Refrigerant piping 10
When the second wall portion (first restricting portion) 115 is arranged on the center side of the first wall portion 113 of No. 3 in a direction substantially orthogonal to the longitudinal direction of the divided body 111, the divided bodies 111 and 112 are superposed, A second opening 116 is provided so as to close the refrigerant pipe 103 and on the upstream side of the air in the second wall 115. The introduction side tank portion 101 is provided with an introduction side tank opening portion 117, and the discharge side tank portion 102 is provided with a discharge side tank opening portion 118.

In the heat exchanger 100 having the above structure, as shown in FIG. 1, the liquid refrigerant flows into the introduction side tank portion 101 through the introduction side tank opening 117, and the refrigerant pipe 103 is changed from the lower side to the upper side. Flowing toward. When the liquid refrigerant flows through the refrigerant pipe 103, the liquid refrigerant absorbs the heat of the air by heat exchange with the air and evaporates and vaporizes. The superheated vaporized refrigerant that has become only the vaporized refrigerant flows from the second opening portion 116 between the first wall portion 113 and the second wall portion 115, flows in parallel with air, and flows from the first opening portion 114 to the discharge side tank portion. Flows through the discharge side tank opening 118 through 102. Further, the air (external fluid) that exchanges heat with the refrigerant is divided into the divided bodies 111 and 112.
The outer sides of and are passed in a direction substantially orthogonal to the longitudinal direction of the heat exchange segment 110.

In the heat exchanger 100 having the above structure, the superheated gas region in the refrigerant pipe 103 has the first wall portion 11
The ratio of the area of the superheated gas area to the heat exchange area of the refrigerant pipe 103, when viewed from the upstream side or the downstream side of the air, corresponds to the portion where the refrigerant between the third wall portion 115 and the third wall portion 115 flows in parallel with the air. Get smaller. For this reason, the ratio of the air passing through the superheated gas region is reduced, and therefore the temperature unevenness of the air passing through the heat exchanger is reduced, which makes it easy to use for comfortable air conditioning.

FIG. 2 is an exploded perspective view of the second embodiment of the heat exchanger according to the present invention. In FIG. 2, the heat exchanger 200 is configured by connecting and stacking a plurality of heat exchange segments 210. The basic structure of the heat exchange segment 210 is the same as that shown in FIG. 1, and the same components are designated by the same reference numerals and the description thereof will be omitted. In FIG. 2, the third wall portion 211 is provided between the introduction side tank portion 101 of the heat exchange segment 210 and the refrigerant pipe 103, and
11 are substantially orthogonal to the longitudinal direction of the divided body 111, 112.
Are provided so as to close the refrigerant pipe 103 when they are overlapped with each other, and the third opening portion 212 is provided on the downstream side of the air in the third wall portion 211. Third wall portion 2 of the refrigerant pipe 103
A fourth wall portion 213 is provided closer to the center than 11 in a direction substantially orthogonal to the longitudinal direction of the divided body 111 so as to close the refrigerant pipe 103 when the divided bodies 111 and 112 are overlapped with each other. The portion 214 is provided on the upstream side of the fourth wall portion 213 with respect to the air.

In the heat exchanger 200 having the above structure, as shown in FIG. 2, the liquid refrigerant flows from the introduction side tank opening 117 into the introduction side tank 101, and from the third opening 212 to the third side. It flows between the wall portion 211 and the fourth wall portion 213, flows in parallel with air, flows from the fourth opening portion 214 to the refrigerant pipe 103, and flows through the refrigerant pipe 103 from the lower side to the upper side. The liquid refrigerant is used for the third wall portion 211 and the fourth wall portion 21.
3 and the refrigerant pipe 103, the heat of the air is absorbed by heat exchange with the air to evaporate and vaporize. The superheated vaporized refrigerant that has become only the vaporized refrigerant flows from the second opening portion 116 between the first wall portion 113 and the second wall portion 115, flows in parallel with air, and flows from the first opening portion 114 to the discharge side tank portion. 10
2 through the discharge side tank opening 118. Further, the air (external fluid) that exchanges heat with the refrigerant is the divided body 11
1 and the outer side of the divided body 112, the heat exchange segment 210
It is configured to pass in a direction substantially orthogonal to the longitudinal direction of the.

In the heat exchanger 200 having the above structure, the superheated gas region in the refrigerant pipe 103 has the first wall portion 11
The ratio of the area of the superheated gas area to the heat exchange area of the refrigerant pipe 103 when viewed from the upstream side or the downstream side of the air when the refrigerant between the third wall portion 115 and the third wall portion 115 flows in parallel with the air is Get smaller. For this reason, the ratio of the air passing through the superheated gas region is reduced, and therefore the temperature unevenness of the air passing through the heat exchanger is reduced, which makes it easy to use for comfortable air conditioning. Further, since the heat exchange segment 210 is composed of the two divided bodies 111 and 112 having the same shape, it is possible to prevent an increase in the assembly process. In addition, since there is only one type of parts, for example, only one type of press molding is required, and capital investment costs can be suppressed, resulting in a large cost reduction effect and comfort in terms of productivity. Easy to use for various air conditioning.

FIG. 3 is an exploded perspective view of a third embodiment of the heat exchanger according to the present invention. In FIG. 3, the heat exchanger 300 is configured by connecting and stacking a plurality of heat exchange segments 310. The basic structure of the heat exchange segment 310 is the same as that shown in FIG. 2, and the same components are designated by the same reference numerals and the description thereof will be omitted. In FIG. 3, a fifth wall portion (second restricting portion) 311 is arranged substantially in the center of the refrigerant pipe 103 of the heat exchange segment 310 so that the divided bodies 111 and 112 are overlapped with each other in a direction substantially orthogonal to the longitudinal direction of the divided body 111. The fifth opening portion 312 is provided on the downstream side of the fifth wall portion 311 in the air direction so as to close the refrigerant pipe 103.

In the heat exchanger 300 having the above structure, as shown in FIG. 3, the liquid refrigerant flows from the introduction side tank opening 117 into the introduction side tank 101 and the third opening 212 to the third side. Flowing between the wall portion 211 and the fourth wall portion 213, flowing in parallel with air, flowing from the fourth opening portion 214 to the refrigerant pipe 103, and flowing through the refrigerant pipe 103 from the fourth opening portion 214 to the fifth opening portion 312, Flow from the fifth opening 312 to the second opening 116 from the lower side to the upper side. When the liquid refrigerant flows between the third wall portion 211 and the fourth wall portion 213 and the refrigerant pipe 103, the liquid refrigerant absorbs the heat of the air by heat exchange with the air and evaporates and vaporizes. The superheated vaporized refrigerant that has become only the vaporized refrigerant flows from the second opening portion 116 between the first wall portion 113 and the second wall portion 115, flows in parallel with air, and flows from the first opening portion 114 to the discharge side tank portion. Flows through the discharge side tank opening 118 through 102. Further, air (external fluid) that exchanges heat with the refrigerant passes through the outside of the divided bodies 111 and 112 in a direction substantially orthogonal to the longitudinal direction of the heat exchange segment 310.

In the heat exchanger 300 having the above structure, the superheated gas region in the refrigerant pipe 103 has the first wall portion 11
The ratio of the area of the superheated gas area to the heat exchange area of the refrigerant pipe 103, when viewed from the upstream side or the downstream side of the air, corresponds to the portion where the refrigerant between the third wall portion 115 and the third wall portion 115 flows in parallel with the air. Get smaller. For this reason, the ratio of the air passing through the superheated gas region is reduced, and therefore the temperature unevenness of the air passing through the heat exchanger is reduced. Further, the fifth wall portion 311 prevents the flow of the refrigerant from meandering in the refrigerant pipe 103, preventing the refrigerant from being biased toward the upstream side or the downstream side of the air in the refrigerant pipe 103, and thus the area of the superheated gas area. You can prevent it from expanding. Therefore, the temperature unevenness of the air passing through the heat exchanger is reduced, and it becomes easy to use for comfortable air conditioning. Further, since the heat exchange segment 310 is composed of the two divided bodies 111 and 112 having the same shape, it is possible to prevent an increase in the assembly process. In addition, since there is only one type of parts, for example, only one type of press molding is required, and capital investment costs can be suppressed, resulting in a large cost reduction effect and comfort in terms of productivity. Easy to use for various air conditioning.

FIG. 4 is an exploded perspective view of the fourth embodiment of the heat exchanger according to the present invention. In FIG. 4, the heat exchanger 400 is configured by connecting and stacking a plurality of heat exchange segments 410. The basic structure of the heat exchange segment 410 is the same as that shown in FIG. 2, and the same components are designated by the same reference numerals and the description thereof will be omitted. In FIG. 4, inside the refrigerant pipe 103 of the heat exchange segment 410, an inner fin having a corrugated cross section (heat exchange area enlarging means)
411, the ridges and valleys of which are heat exchange segments 41
It is arranged so as to be substantially parallel to the longitudinal direction of 0.

In the heat exchanger 400 having the above structure, as shown in FIG. 4, the liquid refrigerant flows from the introduction side tank opening 117 into the introduction side tank 101, and from the third opening 212 to the third side. It flows between the wall portion 211 and the fourth wall portion 213, flows in parallel with air, flows from the fourth opening portion 214 to the refrigerant pipe 103, and flows through the refrigerant pipe 103 from the lower side to the upper side. When the liquid refrigerant flows through the refrigerant pipe 103,
Heat is exchanged with the air through the inner fins 411, and the heat of the air is absorbed to evaporate and vaporize. The superheated vaporized refrigerant that has become the vaporized refrigerant only passes through the second opening 116 and the first wall 11
3 and the second wall 115, flowing parallel to the air,
It flows from the first opening 114 through the discharge-side tank section 102 and out through the discharge-side tank opening 118. Further, the air (external fluid) that exchanges heat with the refrigerant is divided into the divided body 111 and the divided body 1.
The outer side of the heat exchange segment 410 is passed in a direction substantially orthogonal to the longitudinal direction of the heat exchange segment 410.

In the heat exchanger 400 having the above structure, the superheated gas region in the refrigerant pipe 103 has the first wall portion 11
The ratio of the area of the superheated gas region to the heat exchange area of the refrigerant pipe is small when viewed from the upstream side or the downstream side of the air when the refrigerant between the third wall portion 115 and the third wall portion 115 flows in parallel with the air. Become. For this reason, the ratio of the air passing through the superheated gas region is reduced, and therefore the temperature unevenness of the air passing through the heat exchanger is reduced. Further, the refrigerant pipe 10
The inner fins 411 provided inside 3 increase the area of the heat exchange surface between the air and the refrigerant, increase the amount of heat exchange in the same time, or exchange the same amount of heat in a shorter time. This makes it possible to compensate for heat exchange in a region having a poor heat exchange capacity, for example, in a superheated gas region, so that the temperature unevenness of the air passing through the heat exchanger is reduced and it becomes easy to use for comfortable air conditioning. Further, since the heat exchange segment 410 is composed of the two divided bodies 111 and 112 having the same shape, it is possible to prevent an increase in the assembly process. In addition, since there is only one type of parts, for example, only one type of press molding is required, and capital investment costs can be suppressed, resulting in a large cost reduction effect and comfort in terms of productivity. Easy to use for various air conditioning.

FIG. 5 is an exploded perspective view of a fifth embodiment of the heat exchanger according to the present invention. In FIG. 5, the heat exchanger 500 is configured by connecting and stacking a plurality of heat exchange segments 510. The basic structure of the heat exchange segment 510 is the same as that shown in FIG. 2, and the same components are designated by the same reference numerals and the description thereof will be omitted. In FIG. 5, a protrusion (refrigerant flow disturbing means) 5 is provided on the refrigerant pipe 103 of the heat exchange segment 510 toward the inside of the refrigerant pipe 103.
A plurality of, for example, four, 11 are bulged and formed on the divided bodies 111 and 112, respectively. These four protrusions 5
All 11 have the same shape, for example, a truncated cone shape as shown in FIG.

In the heat exchanger 500 having the above-described structure, as shown in FIG. 5, the liquid refrigerant flows from the introduction side tank opening 117 into the introduction side tank 101 and from the third opening 212 to the third side. It flows between the wall portion 211 and the fourth wall portion 213, flows in parallel with air, flows from the fourth opening portion 214 to the refrigerant pipe 103, and flows through the refrigerant pipe 103 from the lower side to the upper side. When the liquid refrigerant flows through the refrigerant pipe 103,
The flow is disturbed by the projections 511, heat exchange with the air is performed, and the heat of the air is absorbed to evaporate and vaporize. The superheated vaporized refrigerant that has become only the vaporized refrigerant flows from the second opening portion 116 between the first wall portion 113 and the second wall portion 115, flows in parallel with air, and flows from the first opening portion 114 to the discharge side tank portion. Flows through the discharge side tank opening 118 through 102. Further, air (external fluid) that exchanges heat with the refrigerant passes through the outside of the divided bodies 111 and 112 in a direction substantially orthogonal to the longitudinal direction of the heat exchange segment 510.

In the heat exchanger 500 having the above structure, the superheated gas region in the refrigerant pipe 103 has the first wall portion 11
The ratio of the area of the superheated gas region to the heat exchange area of the refrigerant pipe is small when viewed from the upstream side or the downstream side of the air when the refrigerant between the third wall portion 115 and the third wall portion 115 flows in parallel with the air. Become. For this reason, the ratio of the air passing through the superheated gas region is reduced, and therefore the temperature unevenness of the air passing through the heat exchanger is reduced. Further, the protrusion 511 disturbs the refrigerant flow in the refrigerant pipe 103, promotes heat transfer inside the refrigerant flow, increases the heat exchange amount in the same time, or can exchange the same heat amount in a shorter time. . This makes it possible to compensate for heat exchange in a region having a poor heat exchange capacity, for example, in a superheated gas region, so that the temperature unevenness of the air passing through the heat exchanger is reduced, and it becomes easier to use for comfortable air conditioning. Further, since the heat exchange segment 510 is composed of the two divided bodies 111 and 112 having the same shape, an increase in the number of assembly steps can be prevented. In addition, since there is only one type of parts, for example, only one type of press molding is required, and capital investment costs can be suppressed, resulting in a large cost reduction effect and comfort in terms of productivity. Easy to use for various air conditioning.

FIG. 6 is a development view of essential parts of a sixth embodiment of the heat exchanger according to the present invention. In FIG. 6, the heat exchanger 600 is configured by connecting and stacking a plurality of heat exchange segments 610. The heat exchange segment 610 has the same basic configuration as that shown in FIG. 2, and the same components are designated by the same reference numerals and the description thereof will be omitted. In FIG. 6, the heat exchange segment 610 is configured by bending a second divided body (divided body) 611 formed by pressing and folding it from a folding center 612 and stacking it.

In the heat exchanger 600 having the above structure, the liquid refrigerant flows from the introduction side tank opening 117 into the introduction side tank 101, and from the third opening 212 to the third wall 211 and the fourth wall. It flows to the portion 213, flows in parallel with the air, flows from the fourth opening 214 to the refrigerant pipe 103, and flows through the refrigerant pipe 103 from the lower side to the upper side. The liquid refrigerant exchanges heat with air when flowing through the refrigerant pipe 103, absorbs heat of the air, and evaporates and vaporizes. The superheated vaporized refrigerant that has become only the vaporized refrigerant flows from the second opening portion 116 between the first wall portion 113 and the second wall portion 115, flows in parallel with air, and flows from the first opening portion 114 to the discharge side tank portion. Flows through the discharge side tank opening 118 through 102. Further, the air (external fluid) that exchanges heat with the refrigerant is the second divided body 61.
1 is folded from the bending center 612,
The heat exchange segment 610 passes through in a direction substantially orthogonal to the longitudinal direction.

In the heat exchanger 600 having the above structure, the superheated gas region in the refrigerant pipe 103 has the first wall portion 11
The ratio of the area of the superheated gas region to the heat exchange area of the refrigerant pipe is small when viewed from the upstream side or the downstream side of the air when the refrigerant between the third wall portion 115 and the third wall portion 115 flows in parallel with the air. Become. For this reason, the ratio of the air passing through the superheated gas region is reduced, and therefore the temperature unevenness of the air passing through the heat exchanger is reduced, which makes it easy to use for comfortable air conditioning. Further, the second split body 611 is bent to the bending center 6
Since it is folded from 12 and overlapped,
Since the increase in the assembly process can be prevented and the number of types of parts is one, for example, only one type of press forming mold is required and the capital investment cost can be suppressed, resulting in a large cost reduction effect and productivity. From the aspect, it is easy to use for comfortable air conditioning.

FIG. 7 is an exploded perspective view of essential parts of a seventh embodiment of the heat exchanger according to the present invention. In FIG. 7, the heat exchanger 700 is configured by connecting and stacking a plurality of heat exchange segments 710. The heat exchange segment 710 has the same basic configuration as that shown in FIG. 2, and the same components are designated by the same reference numerals and the description thereof will be omitted. In FIG. 7, the heat exchange segment 710 is the introduction side tank portion 1
A hollow cylinder (hollow body) 711 that becomes 01, a hollow cylinder (hollow body) 712 that becomes the discharge side tank portion 102, and press formed pipe divided bodies 713 and 71 that become the refrigerant pipe 103.
It is composed of four superpositions.

In the heat exchanger 700 having the above structure, as shown in FIG. 7, the liquid refrigerant flows from the introduction side tank opening 117 into the introduction side tank 101, and from the third opening 212 to the third side. It flows between the wall portion 211 and the fourth wall portion 213, flows in parallel with air, flows from the fourth opening portion 214 to the refrigerant pipe 103, and flows through the refrigerant pipe 103 from the lower side to the upper side. When the liquid refrigerant flows through the refrigerant pipe 103,
It exchanges heat with air, absorbs the heat of air and evaporates and vaporizes. The superheated vaporized refrigerant that has become only the vaporized refrigerant flows from the second opening portion 116 between the first wall portion 113 and the second wall portion 115, flows in parallel with air, and flows from the first opening portion 114 to the discharge side tank portion. Flows through the discharge side tank opening 118 through 102.

In the heat exchanger 700 having the above structure, the superheated gas region in the refrigerant pipe 103 has the first wall portion 11
The ratio of the area of the superheated gas region to the heat exchange area of the refrigerant pipe is small when viewed from the upstream side or the downstream side of the air when the refrigerant between the third wall portion 115 and the third wall portion 115 flows in parallel with the air. Become. For this reason, the ratio of the air passing through the superheated gas region is reduced, and therefore the temperature unevenness of the air passing through the heat exchanger is reduced, which makes it easy to use for comfortable air conditioning. Furthermore, a hollow cylinder 71 is provided in the introduction side tank portion 101.
1 and the hollow cylinder 712 for the discharge side tank section 102, the introduction side tank section 101 and the discharge side tank section 1
02 can eliminate the possibility that the thickness will be insufficient,
In the formation of the two pipe divisions 713 and 714, since the two tank parts 101 and 102 on the discharge side and the introduction side are separate parts, the two tank parts 101 on the discharge side and the introduction side, such as deep drawing processing, The 102 forming process is not necessary, the manufacturing is easy, and it is easy to use for comfortable air conditioning.

In the above embodiment, the description has been made by adapting to the case where the corrugated fins are not sandwiched between the heat exchange segments, but the corrugated fins are not sandwiched between the heat exchange segments. The present invention is not limited to this, and can be applied to the one in which corrugated fins are sandwiched between the heat exchange segments.

In the above embodiment, the first opening 114 is located downstream of the air, the second opening 116 is located upstream of the air, and the third opening 212 is located downstream of the air.
The fourth opening 214 is located on the upstream side of the air, and the fifth opening 312 is formed.
Although the position where each opening is provided is not limited to the above position, the first opening 114 is provided on the upstream side of the air, and the second opening 1 is provided.
16 may be provided on the downstream side of air, the third opening 212 may be provided on the upstream side of air, the fourth opening 214 may be provided on the downstream side of air, and the fifth opening 312 may be provided on the upstream side of air. It is a thing.

[0046]

As described above, according to the first aspect of the invention, the direction of the flow of the overheated vaporized refrigerant is parallel to the external fluid by the first restricting portion, so that the external fluid When viewed from the upstream side or the downstream side, the ratio of the area of the superheated gas area to the heat exchange area of the refrigerant pipe becomes small. For this reason, the ratio of the external fluid passing through the superheated gas region is reduced, and therefore, the temperature unevenness of the external fluid passing through the heat exchanger is reduced, and it is easy to use for comfortable air conditioning.

According to the second aspect of the invention, the area of the heat exchange surface between the external fluid and the refrigerant is enlarged by the heat exchange area enlarging means provided inside the refrigerant pipe, and the heat exchange is performed within the same time. The amount can be increased or the same amount of heat can be exchanged in a shorter time. This makes it possible to compensate for heat exchange in a region with poor heat exchange capacity, for example, in the superheated gas region, and thus the temperature unevenness of the external fluid passing through the heat exchanger is reduced, which is effective for comfortable air conditioning. .

According to the third aspect of the invention, the refrigerant flow disturbing means disturbs the refrigerant flow in the refrigerant pipe, promotes heat transfer inside the refrigerant flow, and increases the amount of heat exchange within the same time. Or, the same amount of heat can be exchanged in a shorter time. As a result, it is possible to compensate for heat exchange in a region with poor heat exchange capacity, for example, in the superheated gas region, so the temperature unevenness of the external fluid passing through the heat exchanger is reduced, and it is easier to use for comfortable air conditioning Play.

According to the fourth aspect of the present invention, the second restricting portion prevents the flow of the refrigerant from meandering in the refrigerant pipe, and prevents the refrigerant from being biased to the upstream side or the downstream side of the external fluid in the refrigerant pipe. Therefore, it is possible to prevent the area of the superheated gas area from expanding, and it is possible to achieve comfortable air conditioning and to make it easier to use.

According to the invention of claim 5, the introduction side tank portion, the discharge side tank portion, and the refrigerant pipe have the same shape.
Since it is configured as one divided body, an increase in the assembly process can be prevented. In addition, since there is only one type of parts, for example, capital investment costs during production, such as die cost for press forming, can be suppressed, resulting in a large cost reduction effect, and also in terms of manufacturing and production. It has the effect of making it easy to use for comfortable air conditioning.

According to the invention of claim 6, the introduction side tank portion, the discharge side tank portion and the refrigerant pipe are integrally formed by connecting a part of the two divided bodies, and the connected portion is bent. Since it is configured by stacking, it is possible to prevent an increase in the assembly process, and since there is only one type of parts, it is possible to reduce the capital investment cost during production, such as the die cost for press forming, thus reducing the cost. The reduction effect is large, and in terms of manufacturability, the effect is that comfortable air conditioning is easier to use.

According to the seventh aspect of the invention, since the introduction side tank section and the discharge side tank section are composed of hollow bodies, it is easy to secure the wall thickness of the introduction side tank section and the discharge side tank section. Further, since the two tank parts on the introduction side and the discharge side are separate parts in the formation of the two pipe divisions, for example, the step of forming the two tank parts on the introduction side and the discharge side such as deep drawing becomes unnecessary. It also has the effect of facilitating manufacturing, and also in terms of manufacturability, making it easier to use for comfortable air conditioning.

According to the invention of claim 8, the area of the superheated gas area to the heat exchange area of the refrigerant pipe of the heat exchanger is narrow, and the ratio of the external fluid passing through the superheated gas area can be reduced, so that the heat Since the temperature unevenness of the external fluid passing through the exchanger is reduced, it is possible to provide an air conditioner that realizes comfortable air conditioning.

[Brief description of drawings]

FIG. 1 is a diagram showing an embodiment of a heat exchanger according to the present invention, and is an exploded perspective view of the heat exchanger.

FIG. 2 is a view showing another embodiment of the heat exchanger according to the present invention, and is an exploded perspective view of the heat exchanger.

FIG. 3 is a view showing still another embodiment of the heat exchanger according to the present invention, and is an exploded perspective view of the heat exchanger.

FIG. 4 is a view showing still another embodiment of the heat exchanger according to the present invention, and is an exploded perspective view of the heat exchanger.

FIG. 5 is a view showing still another embodiment of the heat exchanger according to the present invention, and is an exploded perspective view of the heat exchanger.

FIG. 6 is a view showing still another embodiment of the heat exchanger according to the present invention, and is an exploded view of a main part of the heat exchanger.

FIG. 7 is a view showing still another embodiment of the heat exchanger according to the present invention, and is an exploded perspective view of a main part of the heat exchanger.

FIG. 8 is an exploded perspective view showing an example of a conventional heat exchanger.

[Explanation of symbols]

100, 200, 300, 400, 500, 600, 7
00 heat exchanger 101 introduction side tank section 102 discharge side tank section 103 refrigerant pipes 111, 112 divided body 113 first wall section (first restriction section) 115 second wall section (first restriction section) 311 fifth wall Part (second regulation part) 411 Inner fin (heat exchange area expanding means) 511 Protrusion (refrigerant flow disturbing means) 711, 712 Hollow cylinder (hollow body) 713, 714 Pipe division body

─────────────────────────────────────────────────── ─── Continuation of front page (51) Int.Cl. ⁷ Identification code FI theme code (reference) F28F 13/12 F28F 13/12 C

Claims (8)

[Claims] 1. An introduction side tank section and a discharge side tank section,
A refrigerant pipe disposed between the two tank parts on the introduction side and the discharge side to connect the two tank parts, and introduces the refrigerant introduced into the introduction side tank part to the discharge side tank part through the refrigerant pipe. In the process of discharging, an external fluid is caused to flow in a direction substantially orthogonal to the longitudinal direction of the refrigerant pipe so as to come into contact with the outer surface of the refrigerant pipe, and heat exchange is performed between the external fluid and the refrigerant flowing through the refrigerant pipe. Then, in the heat exchanger for evaporating and evaporating the refrigerant, in the refrigerant pipe, a first restricting portion that restricts the flowing direction of the evaporated refrigerant so as to be substantially parallel to the flowing direction of the external fluid is provided. A heat exchanger characterized by being provided. 2. The heat exchanger according to claim 1, wherein a heat exchange area expanding means for expanding a heat exchange area between the external fluid and the refrigerant is provided inside the refrigerant pipe. Heat exchanger to. 3. The heat exchanger according to claim 1, wherein a refrigerant flow disturbing means for disturbing the flow of the refrigerant is provided inside the refrigerant pipe. 4. The heat exchanger according to claim 1, wherein a second restriction portion that causes the flow of the refrigerant to meander is provided substantially at the center of the refrigerant pipe in the longitudinal direction. vessel. 5. The heat exchanger according to claim 1, wherein the discharge-side tank portion, the introduction-side tank portion, and the refrigerant pipe have the same shape divided into two parts in the longitudinal direction of the refrigerant pipe. A heat exchanger characterized in that it is configured as two divided bodies. 6. The heat exchanger according to claim 5, wherein the two divided bodies are unfolded and some of them are joined together to be integrally formed, and the joined portion is bent to form the two pieces.
A heat exchanger characterized by stacking two divided bodies. 7. The heat exchanger according to claim 1, wherein the discharge side tank portion and the introduction side tank portion are hollow bodies, and the refrigerant pipe is divided into two parts in a longitudinal direction of the refrigerant pipe. And a heat exchanger characterized by being configured as two pipe division bodies. 8. An air conditioner comprising the heat exchanger according to any one of claims 1 to 7.