WO2019107001A1

WO2019107001A1 - Heat exchanger

Info

Publication number: WO2019107001A1
Application number: PCT/JP2018/039000
Authority: WO
Inventors: 森本　正和; 西村　健; 河地　典秀; 聡也長沢; 中村　友彦; 一雄亀井; 直人後藤; 佑輔鬼頭; 駿丹野
Original assignee: 株式会社デンソー
Priority date: 2017-11-29
Filing date: 2018-10-19
Publication date: 2019-06-06

Abstract

This heat exchanger (10) is provided with: tubes (100) having a refrigerant passing through the inside thereof; fins (200) which are disposed so as to be adjacent to the tubes; and a cold storage material container (300) which is disposed so as to be adjacent to the tubes in a position on the opposite side from the fins, the cold storage material container containing therein a cold storage material (HM). The tubes include first tubes (110) and second tubes (120) disposed so as to be aligned in the direction through which air passes. The cold storage material container has therein a plurality of ribs (330) that protrude toward the tubes, and a central protruding section (320) that protrudes into a portion that is between the first tubes and the second tubes. Gaps are formed anywhere between the central protruding section and the first tubes, between the central protruding section and the second tubes, and between the central protruding section and the fins.

Description

Heat exchanger

Cross-reference to related applications

This application is based on Japanese Patent Application No. 2017-228891 filed on Nov. 29, 2017, and Japanese Patent Application No. 2018-190748 filed on October 9, 2018. Claiming the benefit of its priority, the entire contents of which patent application is hereby incorporated by reference.

The present disclosure relates to a heat exchanger that cools air by heat exchange with a refrigerant.

Examples of a heat exchanger that cools air by heat exchange with a refrigerant include an evaporator used as part of a refrigeration cycle. In the evaporator, the air is cooled by heat exchange between a refrigerant that evaporates to lower the temperature inside the tube and air that passes through the outside of the tube.

In recent years, a heat exchanger configured to include a cold storage material container has been proposed and has already been put to practical use (see, for example, Patent Document 1 below). The cold storage material container is a container in which a cold storage material such as paraffin is contained, and is disposed in a state of being in contact with a tube through which the refrigerant passes in the heat exchanger. In the heat exchanger provided with the cold storage material container, the temperature of the tube or the like is kept low for a while even after the circulation of the refrigerant is stopped. Therefore, when such a heat exchanger is mounted on a vehicle air conditioner, it is possible to continuously blow low temperature air into the vehicle compartment even in the idle stop state.

As described in Patent Document 1 below, a plurality of ribs (convex portions) are formed on the surface of the cold storage material container, and the tips of the respective ribs are joined to the surface of the tube. As a result, a clearance space is formed between the cold storage material container and the tube (that is, around the rib). Condensed water generated on the surface of the cold storage material container is discharged to the outside through this gap space.

Moreover, in the heat exchanger described in the following patent document 1, two tubes are arrange | positioned so that two tubes may be located in a line along the direction through which air passes. The cool storage material container disposed at a position adjacent to each of the two tubes is further formed with a central convex portion (shutoff portion) which enters into a portion between the two tubes. In the configuration in which such a central convex portion is formed, since the volume of the cold storage material container is increased, it is possible to further enhance the cold storage performance.

Patent No. 5920087

In the heat exchanger described in Patent Document 1, the side surface of the central convex portion is in contact with each of the two tubes. Further, the tip of the central convex portion is in a state of being in contact with a fin provided on the opposite side across the tube.

In such a configuration, the flow of air in the vicinity of the cold storage material container is hindered by the central convex portion. As a result, it is considered that condensation water generated on the surface of the cold storage material container is difficult to be discharged by the flow of air passing through the heat exchanger. That is, the drainage performance of the heat exchanger may be reduced by providing the central convex portion.

An object of the present disclosure is to provide a heat exchanger with high drainage performance while having a configuration in which a central convex portion is formed in a cold storage material container.

A heat exchanger according to the present disclosure is a heat exchanger that cools air by heat exchange with a refrigerant, and a tube through which the refrigerant passes, a fin disposed adjacent to the tube, and a fin opposite to the tube And a regenerator material container, which is disposed adjacent to the tube at the side position and stores the regenerator material inside. The tubes have a first tube and a second tube arranged so as to line up in the direction in which the air passes. The cold storage material container is formed with a plurality of ribs projecting toward the tube and a central convex portion projecting toward a portion between the first tube and the second tube. A gap is formed between the central convex portion and the first tube, between the central convex portion and the second tube, and between the central convex portion and the fin.

In the heat exchanger having such a configuration, gaps are formed between the central convex portion and the first tube, between the central convex portion and the second tube, and between the central convex portion and the fins. The central convex portion of the cold storage material container is formed to be in the closed state. Air passing through the heat exchanger can flow in the vicinity of the cold storage material container through the respective gaps. As a result, the condensed water generated on the surface of the cold storage material container is easily discharged to the outside by the flow of air as described above. As described above, in the heat exchanger of the above configuration, the flow of air is not impeded by the central convex portion of the cold storage material container, so that the drainage performance can be sufficiently ensured.

According to the present disclosure, it is possible to provide a heat exchanger with high drainage performance while having a configuration in which the central convex portion is formed in the cold storage material container.

FIG. 1 is a view showing an entire configuration of a heat exchanger according to the first embodiment. FIG. 2 is a view showing a part of the II-II cross section of FIG. FIG. 3 is a view showing the configuration of a cold storage material container provided in the heat exchanger of FIG. FIG. 4 is a view showing the configuration of a cold storage material container provided in the heat exchanger according to the second embodiment. FIG. 5 is a view showing the configuration of the heat exchanger according to the third embodiment. FIG. 6 is a view showing the configuration of a cold storage material container provided in the heat exchanger according to the fourth embodiment. FIG. 7: is a figure which shows the structure of a cool storage material container with which the heat exchanger which concerns on the modification of 4th Embodiment is provided. FIG. 8 is a view showing the configuration of a cold storage material container provided in a heat exchanger according to another modification of the fourth embodiment. FIG. 9 is a view showing the configuration of the heat exchanger according to the fifth embodiment. FIG. 10 is a view showing the configuration of a cold storage material container provided in the heat exchanger according to the sixth embodiment. FIG. 11 is a view showing the configuration of the heat exchanger according to the sixth embodiment. FIG. 12 is a view schematically showing a state in which freezing starts to occur around the rib. FIG. 13 is a diagram showing a part of FIG. 10 in an enlarged manner. FIG. 14: is a figure which shows typically the positional relationship of a tube and a cool storage material container. FIG. 15 is a view showing the configuration of a cold storage material container provided in the heat exchanger according to the seventh embodiment.

Hereinafter, the present embodiment will be described with reference to the attached drawings. In order to facilitate understanding of the description, the same constituent elements in the drawings are denoted by the same reference numerals as much as possible, and redundant description will be omitted.

The first embodiment will be described. The heat exchanger 10 according to the present embodiment is configured as an evaporator that forms a part of a refrigeration cycle (not shown) configured as an air conditioning system of a vehicle. A refrigerant is fed to the heat exchanger 10 by a compressor (not shown) disposed in a part of the refrigeration cycle. The compressor is operated by the driving force of an internal combustion engine provided in a vehicle. The heat exchanger 10 cools the air by performing heat exchange between the refrigerant and the air while evaporating the refrigerant sent therein.

The configuration of the heat exchanger 10 will be described with reference to FIG. The heat exchanger 10 includes an upper tank 11, a lower tank 12, a tube 100, a fin 200, and a cold storage material container 300.

The upper tank 11 is a container for temporarily storing the refrigerant supplied to the heat exchanger 10 and supplying the refrigerant to the respective tubes 100. The upper tank 11 is formed as an elongated rod-like container. The upper tank 11 is disposed at the upper side portion of the heat exchanger 10 in a state in which the longitudinal direction thereof is parallel to the horizontal direction.

The lower tank 12 is a container having substantially the same shape as the upper tank 11. The lower tank 12 receives the refrigerant coming from the upper tank 11 through the tube 100. The lower tank 12 is disposed in the lower portion of the heat exchanger 10 in a state in which the longitudinal direction is parallel to the horizontal direction as the upper tank 11 is.

The tube 100 is an elongated tube having a flat cross section, and a plurality of the heat exchangers 10 are provided. Inside the tube 100, a plurality of flow paths FP (not shown in FIG. 1, see FIG. 2) along the longitudinal direction are formed. The respective tubes 100 have their longitudinal direction along the vertical direction, and are stacked and arranged in such a manner that their main surfaces are opposed to each other. The direction in which the plurality of stacked tubes 100 are arranged is the same as the longitudinal direction of the upper tank 11.

One end of each tube 100 is connected to the upper tank 11 and the other end is connected to the lower tank 12. With such a configuration, the internal space of the upper tank 11 and the internal space of the lower tank 12 are communicated with each other by the flow paths FP in the respective tubes 100.

The refrigerant moves from the upper tank 11 to the lower tank 12 through the inside of the tube 100 (that is, the flow path FP). At that time, heat exchange is performed with the air passing through the outside of the tube 100, whereby the refrigerant changes from the liquid phase to the gas phase. In addition, air is deprived of heat by heat exchange with the refrigerant to reduce its temperature. The air to be subjected to heat exchange is fed to the heat exchanger 10 by a fan (not shown) disposed in the vicinity of the heat exchanger 10. The direction in which air is fed is the direction from the back side to the front side in the drawing of FIG. 1 (the y direction described later).

The fins 200 are formed by bending a metal plate in a wave shape, and are disposed between the respective tubes 100. That is, they are disposed adjacent to the tube 100. The fins 200 are so-called "corrugated fins". The top of each of the fins 200, which is corrugated, abuts against the outer surface of the tube 100 and is brazed. Therefore, the heat of the air passing through the heat exchanger 10 is transferred not only to the refrigerant through the tube 100 but also to the refrigerant through the fins 200 and the tube 100. That is, the contact area with air is increased by the fins 200, and heat exchange between the refrigerant and the air is efficiently performed.

The fin 200 is the whole of the space (except for the portion where the cold storage material container 300 described later is disposed) formed between two tubes 100 adjacent to each other along the left-right direction of FIG. It is disposed over the entire range from 11 to the lower tank 12. However, in FIG. 1, only a part thereof is illustrated, and the other parts are omitted.

In addition, after the internal space of the upper tank 11 and the internal space of the lower tank 12 are divided into a plurality by the partition plate, the refrigerant reciprocates between the upper tank 11 and the lower tank 12 (that is, both) Flow) may be used. In realizing the contrivance of the configuration of the heat exchanger 10 described below, the direction and the route through which the refrigerant passes are not particularly limited.

In FIG. 1, the x-axis is set with the direction from the left side to the right side in FIG. 1 being the longitudinal direction of the upper tank 11 as the x direction. Further, the y-axis is set with the direction from the back side to the front side in the drawing of FIG. 1 as a direction in which the air passes through the heat exchanger 10 as the y direction. Furthermore, the z axis is set with the direction from the lower tank 12 to the upper tank 11, that is, the direction from the lower side to the upper side as the z direction. The x-axis, the y-axis, and the z-axis are similarly set in the following drawings.

The cold storage material container 300 is a container disposed adjacent to the tube 100 along the x-axis, and accommodates the cold storage material HM (not shown in FIG. 1, see FIG. 2) inside. When viewed from the tube 100 next to the cool storage material container 300, the cool storage material container 300 is disposed adjacent to the tube 100 at a position opposite to the fins 200.

The cold storage material container 300 is for storing cold when the refrigerant is circulating in the refrigeration cycle including the heat exchanger 10, and keeping the tubes 100 and the like at a low temperature even after the circulation of the refrigerant is stopped. The cold storage material container 300 is formed as an elongated plate-like container. The cold storage material container 300 is disposed at a position between two tubes 100 adjacent to each other, with the longitudinal direction in the z direction. The cold storage containers 300 are joined and held to the respective tubes 100 on both sides thereof.

As shown in FIG. 1, in a plurality of spaces formed between the tube 100 and the tube 100, fins 200 are disposed in a part thereof, and a cold storage material container 300 is disposed in another part thereof. ing. In the present embodiment, the fins 200, the fins 200, and the cold storage material container 300 are regularly arranged in this order from the left side. However, the relative positional relationship between the fins 200 and the cold storage material container 300 and the presence or absence of regularity in the arrangement thereof are not particularly limited.

When the refrigerant is circulating, the cold storage material container 300 is cooled by the tube 100. At this time, the cold storage material HM contained in the cold storage material container 300 is cooled to lower its temperature, and is solidified.

Thereafter, when the vehicle enters the idle stop state, the compressor of the refrigeration cycle stops. Therefore, the circulation of the refrigerant in the refrigeration cycle is not performed, and the evaporation of the refrigerant in the heat exchanger 10 is not performed.

However, since the cold storage material HM at this time is in a solidified state, the cold storage material container 300 and the tubes 100 and the fins 200 disposed in the vicinity thereof are maintained at low temperatures. Therefore, even if the circulation of the refrigerant is stopped, the air passing through the heat exchanger 10 is cooled. Thus, the heat storage material container 300 is disposed, so that the heat exchanger 10 can maintain its cooling performance for a while even after transition to the idle stop state.

More specific configurations of the tube 100 and the cold storage material container 300 will be described with reference to FIGS. 2 and 3. FIG. 2 shows a part of the II-II cross section of FIG. 1, and specifically shows the respective cross sections of one cold storage material container 300 and the tubes 100 on both sides thereof. . In FIG. 2, fins 200 on both sides of the tube 100 are also illustrated. FIG. 3 is a view showing the appearance of the cold storage material container 300 as viewed along the x-axis.

As shown in FIG. 2, each tube 100 aligned along the x-axis includes a first tube 110 and a second tube 120. The pair of first tubes 110 and second tubes 120 are arranged along one side of the cool storage material container 300 along the y direction (that is, the direction in which the air passes through the heat exchanger 10). In FIG. 2, a pair of first tubes 110 and a second tube 120 aligned along the surface of the cold storage material container 300 in the x direction, and a pair of the first tubes 110 and the second tube aligned along the surface in the −x direction. The tubes 120 are shown respectively.

The first tube 110 and the second tube 120 aligned along one side of the cool storage material container 300 are separated from each other. A portion of the cold storage material container 300 facing the space between the first tube 110 and the second tube 120 protrudes toward the space. The portion that protrudes outward in this manner is hereinafter also referred to as "central convex portion 320". The central convex portion 320 can be said to be a portion that protrudes toward the portion between the first tube 110 and the second tube 120.

The central convex portion 320 is a surface on the x-direction side and a surface on the -x-direction side at a position at the center in the y direction (that is, at a position along the air passing direction) Each is formed. Further, as shown in FIG. 3, the central convex portion 320 is formed to extend along the z-axis (that is, along the up-down direction).

The center convex part 320 is formed by making a part of board material which comprises the cool storage material container 300 project outside. Therefore, the space inside the central convex portion 320 is filled with the cold storage material HM. In the cool storage material container 300, the formation of such a central convex portion 320 sufficiently secures the volume (that is, the amount of the cool storage material HM) without wasting the space between the tubes 100. .

In addition, the formation of the central convex portion 320 causes excessive flow of air along the y direction in the space between the cool storage material container 300 and the tube 100 (that is, the gap space GP described later). Can also be obtained. Thereby, it is possible to prevent the cold storage material HM solidified inside the cold storage material container 300 from being heated too much by air and melting early. In view of this point, the protrusion height of the central protrusion 320 along the x axis is preferably larger than the protrusion height of the rib 330 described next.

As shown in FIG. 3, in the cold-storage material container 300, a plurality of ribs 330 are also formed in addition to the central convex portion 320 described above. Each rib 330 is formed to project along the x-axis toward the tube 100 facing the cold storage material container 300. The rib 330 is formed by projecting a part of the plate material of the cold storage material container 300 to the outside similarly to the central convex portion 320. Therefore, the space inside the rib 330 is also filled with the cold storage material HM.

The tip surface of each rib 330 is bonded to the surface of the tube 100. Thereby, the cool storage material container 300 is fixed to the tube 100. With such a configuration, a space is formed between the cold-storage material container 300 and the tube 100 adjacent to each other, that is, around the rib 330. Hereinafter, this space is also referred to as “gap space GP”. The height of the gap space GP along the x direction is equal to the protruding height of the rib 330 along the same direction.

As shown in FIG. 3, the plurality of ribs 330 are formed along the vertical direction on each of the y direction side and the −y direction side of the central convex portion 320.

Each rib 330 formed on the y direction side of the central convex portion 320 is formed to extend from the central convex portion 320 toward an end portion on the y direction side of the cool storage material container 300. Similarly, the respective ribs 330 formed on the −y direction side of the central convex portion 320 are formed to extend from the central convex portion 320 toward the end of the cool storage material container 300 on the −y direction side. ing. Each rib 330 also extends in the downward direction toward the end of the cold storage material container 300 from the central convex portion 320.

The respective ribs 330 and the central convex portion 320 are connected to each other. Here, “connected” means that no gap is formed between the rib 330 and the central convex portion 320, and a boundary portion between the rib 330 and the central convex portion 320 in the cool storage material container 300. Is projecting along the x-axis in the same direction as the ribs 330 and the like.

Each rib 330 is arranged to align along the z-axis. In the present embodiment, the directions in which the respective ribs 330 extend toward the end of the cold storage material container 300 are parallel to one another.

As shown in FIG. 2, in the present embodiment, the protrusion height of the central protrusion 320 along the x-axis is larger than the protrusion height of the rib 330 along the same direction. However, the central protrusion 320 is not in contact with any of the first tube 110 and the second tube 120 on both sides along the y-axis. Further, the central convex portion 320 is not in contact with the fin 200 disposed at a position facing the tip. Therefore, air passes between the central projection 320 and the first tube 110, between the central projection 320 and the second tube 120, and between the central projection 320 and the fin 200. A gap is formed.

In FIG. 3, only the central convex portion 320 and the rib 330 formed on the x-direction side surface of the cool storage material container 300 are shown. However, on the −x direction side surface of the cool storage material container 300 Also, a central convex portion 320 and a rib 330 similar to those shown in FIG. 3 are formed.

The effect of the cold storage material container 300 being formed as described above will be described. When evaporation of the refrigerant and cooling of the air are performed in the heat exchanger 10, dew condensation occurs on the surface of the cold storage material container 300 and the like, whereby dew condensation water is generated in the gap space GP. The dew condensation water WT may stay on the surface of the cold storage material container 300 or the tube 100, and may block the flow of air. As a result, the efficiency of heat exchange in the heat exchanger 10 may be reduced. In order to prevent such a phenomenon, it is preferable that the heat exchange performance of the heat exchanger 10 be high.

Therefore, in the present embodiment, as described above, between the central projection 320 and the first tube 110, between the central projection 320 and the second tube 120, and between the central projection 320 and the fin 200. In each case, a gap through which air passes is formed. In such a configuration, air flowing in the clearance space GP in the y direction can pass through the respective clearances and pass through the vicinity of the central convex portion 320. In FIG. 2, the path through which air passes is indicated by an arrow in this manner. In addition, although a part of the arrow which shows the said path | route is drawn so that the rib 330 may be penetrated, this shows the path | route which passes between the ribs 330 adjacent to each other.

Condensed water staying on the surface of the cold storage material container 300 or the like in the gap space GP is discharged to the outside by the flow of air as described above. As described above, in the heat exchanger 10 according to the present embodiment, the flow of the air is not blocked by the central convex portion 320. Therefore, the central convex portion 320 is formed to sufficiently secure the volume of the cold storage material container 300. However, it is possible to secure sufficient drainage performance of the heat exchanger 10.

In order to obtain such an effect sufficiently, it is preferable that the range of the central convex portion 320 extending along the vertical direction is a range that includes the range from the upper end to the lower end of the tube 100. That is, the z coordinate of the upper end of the central convex portion 320 is equal to or greater than the z coordinate of the upper end of the tube 100, and the z coordinate of the lower end of the central convex portion 320 is equal to or less than the z coordinate of the lower end of the tube 100 Is preferred.

Another effect of forming the central projection 320 so as to extend in the vertical direction will be described. As shown in FIG. 2, the inner fins 310 are accommodated in the cold storage material container 300 of the present embodiment. Heat transfer between the cold storage material container 300 and the cold storage material HM is performed more efficiently by the inner fins 310. When viewed along the z-axis as shown in FIG. 2, the inner fins 310 are disposed in a range extending substantially the whole of the space SP formed inside the cold storage material container 300.

However, the inner fin 310 does not exist in a portion of the space SP inside the central convex portion 320. For this reason, the space inside the central protrusion 320 is a space extending linearly along the z-axis, and the middle fin is not divided by the inner fin 310.

Similarly, the inner fin 310 does not exist in the portion of the space SP inside the rib 330. For this reason, the space inside each rib 330 is a space extending linearly along the longitudinal direction of the rib 330, and the middle fin is not divided by the inner fin 310.

In FIG. 3, reference numeral 301 is a portion serving as an injection port for injecting the cold storage material HM into the cold storage material container 300 when the cold storage material container 300 is manufactured. Hereinafter, the portion is also referred to as “inlet 301”. The inlet 301 is formed at a position further to the z direction side than the z direction side end of the central convex portion 320.

A portion of the refrigerant injected from the inlet 301 into the interior of the cold storage material container 300 moves downward through the path inside the central convex portion 320. Since the path is not divided by the inner fins 310 as described above, the refrigerant can flow smoothly to the lower end of the cold storage material container 300.

As described above, in the present embodiment, the respective ribs 330 and the central convex portion 320 are connected to each other. For this reason, a part of the refrigerant moving downward through the inner path of the central protrusion 320 flows into the space inside the rib 330 and moves in the path along the longitudinal direction of the rib 330. Since the path is not divided by the inner fins 310 as well, the refrigerant can flow smoothly to the y-direction end and the −y-direction end of the cold storage material container 300. In FIG. 3, as described above, a part of the path through which the refrigerant flows is indicated by the arrow.

As described above, even if the positional displacement or the like of the inner fin 310 occurs inside the cool storage material container 300, the route through which the refrigerant flows is always secured without being divided by the inner fin 310. Therefore, it is possible to always smoothly inject the refrigerant into the cold storage material container 300 and complete the injection in a short time.

In the above-mentioned example, each rib 330 was formed as a projection shaped to extend linearly. Alternatively, each rib 330 may be formed as, for example, a circular protrusion.

The second embodiment will be described. In the following, differences from the first embodiment will be mainly described, and descriptions of points in common with the first embodiment will be omitted as appropriate.

In FIG. 4, a part of the cool storage material container 300 according to the present embodiment is drawn as seen from the x direction side as in FIG. 3. As shown in the figure, in the present embodiment, the ribs 330 formed on the -y direction side of the central convex portion 320 move upward from the central convex portion 320 toward the end in the -y direction. It is formed to extend in the direction toward the side. On the other hand, the respective ribs 330 formed on the y direction side of the central convex portion 320 are lower side closer to the end portion on the y direction side from the central convex portion 320 as in the first embodiment (FIG. 3) It is formed to extend in the direction of

As described above, even when the ribs 330 are formed to extend in a direction different from the downward direction toward the end, the same effect as that described in the first embodiment can be obtained. Play.

In the present embodiment, the dew condensation water moves to the y direction side along the surface of the inclined rib 330 also in the portion on the −y direction side with respect to the central protrusion 320. Such movement of condensed water is likely to be promoted by the flow of air along the y direction. For this reason, it is possible to further improve the drainage performance of the heat exchanger 10.

A third embodiment will be described. In the following, differences from the first embodiment will be mainly described, and descriptions of points in common with the first embodiment will be omitted as appropriate.

FIG. 5 shows the configuration of the heat exchanger 10 according to the present embodiment by a cross-sectional view drawn from the same viewpoint as FIG. 2. As shown in the figure, in the present embodiment, the protrusion height of the rib 330 along the x-axis and the protrusion height of the central protrusion 320 along the same direction are the same. Even in such a configuration, the same effects as those described in the first embodiment can be obtained. Furthermore, in the present embodiment, by making the protruding height of the central protrusion 320 lower than in the case of the first embodiment, the flow of air passing through the gap space GP is further less likely to be blocked by the central protrusion 320. As a result, an effect is obtained that the drainage performance of the heat exchanger 10 is further enhanced.

A fourth embodiment will be described. In the following, differences from the first embodiment will be mainly described, and descriptions of points in common with the first embodiment will be omitted as appropriate.

FIG. 6 is a view showing the appearance of the cool storage material container 300 according to the present embodiment as viewed along the x-axis. As shown in the figure, in the cool storage material container 300 according to the present embodiment, an end-side convex portion 321 is formed separately from the central convex portion 320. The end-side convex portion 321 is formed by projecting a part of the plate material constituting the cold storage material container 300 to the outside along the x-axis, similarly to the central convex portion 320 and the rib 330. The end-side convex portion 321 is formed to extend along the z-axis similarly to the central convex portion 320. Further, the end-side convex portions 321 are formed so as to connect the y-direction end portions of the ribs 330 formed on the y-direction side with respect to the central convex portion 320.

Although illustration is omitted, the inner fin 310 does not exist in a portion of the space SP on the inner side of the end-side convex portion 321. For this reason, the space inside the end-side convex portion 321 is a space extending linearly along the z-axis, and the middle thereof is not divided by the inner fin 310.

For this reason, a part of the refrigerant injected from the injection port 301 into the inside of the cold storage material container 300 moves downward through the path inside the end-side convex portion 321. Since the path is not divided by the inner fins 310 as described above, the refrigerant can flow smoothly to the lower end of the cold storage material container 300.

As described above, in the present embodiment, by forming the end-portion-side convex portion 321, the passage path of the refrigerant injected into the cold storage material container 300 is further increased. For this reason, it becomes possible to perform the injection of the refrigerant into the inside of the cool storage material container 300 more smoothly.

A modification of the present embodiment will be described with reference to FIG. As in the modification shown in the figure, the end-side convex portion 321 may be formed at a position on the −y direction side. That is, the end-side convex portions 321 may be formed to connect the end portions on the -y direction side of the respective ribs 330 formed on the -y direction side with respect to the central convex portion 320.

Another modification of the present embodiment will be described with reference to FIG. As in the modification shown in the figure, the end-side convex portions 321 may be formed at both the position in the y direction and the position in the −y direction. That is, the end-side convex portion 321 connecting the y-direction end portions of the ribs 330 formed on the y-direction side with respect to the central convex portion 320 and the −y-direction side relative to the central convex portion 320 It is good also as composition which has both the end side convex part 321 which connects the end parts by the side of-y of each of these ribs 330.

A fifth embodiment will be described. In the following, differences from the first embodiment will be mainly described, and descriptions of points in common with the first embodiment will be omitted as appropriate.

FIG. 9 shows the configuration of the heat exchanger 10 according to the present embodiment by a cross-sectional view drawn from the same viewpoint as FIG. As shown in the figure, in the present embodiment, a pair of first tubes 110 and second tubes 120 aligned along the y-axis are connected to each other via a plate-like connection portion 130. The tube 100 having the first tube 110, the second tube 120, and the connecting portion 130 can be integrally formed, for example, by extrusion. Thus, even if the first tube 110 and the second tube 120 are not separated from each other, the same effects as those described in the first embodiment can be obtained.

A sixth embodiment will be described. In the following, differences from the first embodiment will be mainly described, and descriptions of points in common with the first embodiment will be omitted as appropriate.

FIG. 10 shows the appearance of the cool storage material container 300 according to the present embodiment as viewed along the x-axis. What is shown in FIG. 11 is a cross-sectional view of the configuration of the heat exchanger 10 according to the present embodiment, drawn from the same viewpoint as FIG.

As shown in FIG. 10, in the cool storage material container 300, the position to be the end along the air passing direction (that is, the y direction) will be referred to as “end E1” and “end E2” below. It is written as In the above, “the end along the air passing direction” includes both the upstream end and the downstream end in the air flow direction.

The end E1 is the y-direction side of the cold storage material container 300, that is, the downstream end along the air passing direction. The end E2 is an end on the -y direction side of the cool storage material container 300, that is, the upstream end along the direction in which the air passes.

The respective ribs 330 formed on the y-direction side of the central convex portion 320 are formed to extend from the central convex portion 320 toward the end E1. The width along the up and down direction of these ribs 330 decreases as they approach the end E1.

Similarly, the respective ribs 330 formed on the −y direction side of the central convex portion 320 are formed to extend from the central convex portion 320 toward the end E2. The width along the up and down direction of these ribs 330 decreases as they approach the end E2.

In the present embodiment, the shape and arrangement of the ribs 330 arranged on the y direction side of the central protrusion 320 and the shape and arrangement of the ribs 330 arranged on the −y direction side of the central protrusion 320 are mutually symmetrical. It has become. Further, although only the central convex portion 320 and the rib 330 formed on the surface in the x direction of the cold storage material container 300 are shown in FIG. 10, the surface on the −x direction side of the cold storage material container 300 is shown. Also, a central convex portion 320 and a rib 330 similar to those shown in FIG. 10 are formed.

For convenience of explanation, the distance along the up and down direction of the pair of ribs 330 adjacent to each other is hereinafter referred to as “vertical distance”. In the present embodiment, the width of each rib 330 gradually decreases from the center convex portion 320 side to the end E1 (or end E2) side as described above, so that the above-mentioned vertical interval is The distance from the central convex portion 320 to the end E1 (or the end E2) increases.

The effect that the rib 330 of such a shape is formed in the cool storage material container 300 is demonstrated, referring FIG. What is shown in FIG. 12A is a state in which the dew condensation water freezes between a pair of ribs 330 adjacent to each other among the plurality of ribs 330 in the present embodiment. What is shown in FIG. 12B is a state in which the dew condensation water freezes between a pair of ribs 330 adjacent to each other among the plurality of ribs 330 in the comparative example.

In the comparative example shown in FIG. 12 (B), the width along the vertical direction of each rib 330 is uniform throughout. For this reason, the vertical interval which is the interval between the ribs 330 adjacent to each other is also uniform from the central protrusion 320 side to the end E1 side as a whole.

In the heat exchanger 10 provided with the cold storage material container 300 having such a configuration, condensation occurs on the surface of the cold storage material container 300 when evaporation of the refrigerant is performed, so that condensation water (of liquid) is generated in the gap space GP. WT occurs. When the temperature of the refrigerant decreases to 0 ° C. or less, the dew condensation water WT is frozen, whereby ice C is generated in the gap space GP.

Ice C is generated starting from the portion where the cold storage material container 300 and the tube 100 are joined, that is, the tip portion of the rib 330, and tends to grow from there to the periphery. The state in the middle of the process in which the ice C is thus grown is schematically shown in FIG. 12 (B).

In the comparative example, as described above, the vertical distance from the central convex portion 320 to the end E1 is uniform. In such a configuration, in the process of growing the ice C generated at the tip portion of the rib 330, as shown in FIG. 12B, the condensed water WT of the liquid is trapped inside the ice C. There are times when

The dew condensation water WT trapped inside the ice C is also cooled and frozen thereafter. However, since the condensation water WT is frozen in a closed space, a large volumetric expansion force is applied to the surrounding tube 100 and the cold storage material container 300 by the expansion of the condensation water WT during freezing. There are times when As a result, there is a possibility that a part of the tube 100, the cold storage material container 300 and the like may be damaged.

In order to prevent such breakage, it is also conceivable to increase the protruding height of each rib 330 to a certain extent to sufficiently enhance the drainage performance of the gap space GP. However, when the protruding height of each rib 330 is increased, the volume of the cold storage material container 300 disposed in the limited space is reduced. In this case, the amount of the cold storage material HM stored in the cold storage material container 300 decreases, and the function of cold storage is only exhibited for a short time, which is not preferable.

So, in this embodiment, it is supposed that breakage of the cool storage material container 300 accompanying freezing as mentioned above is prevented by devising the shape of the rib 330. As shown in FIG.

In the present embodiment shown in FIG. 12A, the vertical interval gradually increases from the central convex portion 320 side toward the end E1 side (or the end E2 side). Therefore, even after the growth of ice C starts, the end E1 side is not closed by the ice C, and the dew condensation water WT can be discharged from the portion to the outside.

In the configuration shown in FIG. 12A, the ice C grows from the central convex portion 320 side toward the end E1 side. As a result, the dew condensation water WT on the end E1 side becomes ice C later (that is, finally) than the other part, so that the inside condensation water WT is not trapped. For this reason, as in the comparative example of FIG. 12B, the volumetric expansion force due to freezing does not act on the members such as the tube 100 and the like.

As described above, in the heat exchanger 10 according to the present embodiment, the width of the respective ribs 330 along the vertical direction is smaller as it gets closer to the end E1 (or the end E2), the condensed water WT Damage to the parts due to the freezing of the In addition, since it is not necessary to make the height of the rib 330 higher than necessary, the volume of the cold storage material container 300 is not sacrificed.

The above-described configuration, that is, the configuration in which the width along the vertical direction of each rib 330 becomes smaller toward the end E1 (or the end E2) is the first embodiment described above. It can be adopted in any of the heat exchangers 10 from the embodiment to the fifth embodiment.

As shown in the enlarged view of FIG. 13, in the present embodiment, the vertical distance L12 at the position closest to the end E1 (or the end E2) is at the most central position along the air flow direction. It is 1.5 times the vertical interval L11. According to the results confirmed by the present inventors through experiments etc., if the vertical distance L12 on the end side is maintained at least 1.5 times the vertical distance L11 on the central side, the condensed water WT is inside the ice C It has been found that the phenomenon of being trapped inside can be reliably prevented.

The above-described configuration, that is, the configuration in which the vertical distance L12 on the end side is 1.5 times or more the vertical distance L11 on the central side is the first to fifth embodiments described above. It can be adopted in any heat exchanger 10 up to.

As shown in FIGS. 10 and 13, the ribs 330 in this embodiment all extend downward as approaching the end E1 (or the end E2) from the central convex portion 320. . In such a configuration, the dew condensation water WT of the liquid existing between the ribs 330 is easily discharged to the end side by gravity. Therefore, the phenomenon that the condensed water WT is trapped inside the ice C is further prevented. Among the plurality of ribs 330, those which are formed so as to extend in the downward direction toward the end side may be all the ribs 330 as in this embodiment, and some of the ribs Only 330 may be sufficient.

As shown in FIGS. 10 and 13, the ribs 330 in the present embodiment are all connected to the central protrusion 320. For this reason, compared with the structure which the rib 330 does not connect with the center convex part 320, the volume of the cool storage material container 300 is ensured still larger. Thereby, the cooling performance of the cool storage material container 300 can be exhibited over a long time.

Other configurations will be described. The structure in the vicinity of the center convex part 320 among the heat exchangers 10 which concern on this embodiment is typically shown by FIG. In the figure, illustration of the rib 330 is omitted.

In the same figure, reference numeral 101 is attached to an end of the tube 100 (specifically, the second tube 120) on the central convex portion 320 side. Hereinafter, the end is also referred to as “end 101”. The distance between the end 101 and the central protrusion 320 is shown as "L13" in FIG. This L13 can be said to be the shortest distance between the central projection 320 and the tube 100. The gap formed between the central convex portion 320 and the tube 100 is hereinafter also referred to as a “gap GPa”.

In FIG. 14, the protruding height of the rib 330 (not shown), that is, the height of the clearance space GP along the x axis is indicated as “L14”. In the present embodiment, a distance L13 between the central convex portion 320 and the tube 100 is larger than a projection height L14 of the rib 330.

If L13 is smaller than L14, freezing may be completed at a relatively early stage in the portion between the end 101 and the central convex portion 320. In this case, condensation water (liquid) existing in the vicinity of the end portion 101 and inside the gap space GP may be trapped by the ice generated between the end portion 101 and the central convex portion 320. . That is, the discharge of the condensed water WT as described with reference to FIG. 12A may be hindered by the ice.

However, in the present embodiment, since L13 is larger than L14, the space between the end portion 101 and the central convex portion 320 is not blocked by ice at an early stage. For this reason, also in the vicinity of the end portion 101, the phenomenon that the member is damaged due to the volumetric expansion force of the confined dew condensation water is reliably prevented.

As described above, in the present embodiment, the gap GPa is formed between the central convex portion 320 and the tube 100. As a result, condensed water is discharged to the outside from the gap GPa also in the portion of the rib 330 on the central convex portion 320 side. In addition, since L13 which is the distance between the central convex portion 320 and the tube 100 is larger than L14 which is the protruding height of the rib 330, the gap GPa is prevented from being blocked by ice. It is done.

The above-described configuration, that is, the configuration in which L13 is larger than L14, can be employed in any of the heat exchangers 10 of the first to fifth embodiments described above.

A seventh embodiment will be described with reference to FIG. In the following, points different from the sixth embodiment described above will be mainly described, and descriptions of points in common with the sixth embodiment will be omitted as appropriate.

In FIG. 15, a part of the cool storage material container 300 according to the present embodiment is drawn as seen from the x direction side as in FIG. As shown in the figure, in the present embodiment, the respective ribs 330 formed on the -y direction side of the central convex portion 320 move upward as they approach the end E2 from the central convex portion 320. It is formed to extend to On the other hand, in the same way as in the sixth embodiment (FIG. 13), the ribs 330 formed on the y-direction side of the central convex portion 320 are directed downward as they approach the end E1 from the central convex portion 320. It is formed to extend to

As described above, even when the ribs 330 are formed to extend in a direction different from the direction toward the lower side toward the end, the same effects as those described in the sixth embodiment can be obtained. Play.

The present embodiment has been described above with reference to the specific example. However, the present disclosure is not limited to these specific examples. Those appropriately modified in design by those skilled in the art are also included in the scope of the present disclosure as long as the features of the present disclosure are included. The elements included in the above-described specific examples, and the arrangement, conditions, and shapes thereof are not limited to those illustrated, but can be appropriately modified. The elements included in the above-described specific examples can be appropriately changed in combination as long as no technical contradiction arises.

Claims

A heat exchanger (10) for cooling air by heat exchange with a refrigerant,
A tube (100) through which the refrigerant passes, and
A fin (200) disposed adjacent to the tube;
And a regenerator material container (300) which is disposed adjacent to the tube at a position opposite to the fins and which accommodates a regenerator material (HM) therein.
The tubes have a first tube (110) and a second tube (120) arranged to line up with the direction of air passage.
In the cold storage material container,
A plurality of ribs (330) projecting towards the tube;
A central projection (320) is formed which protrudes toward the portion between the first tube and the second tube,
A thermal gap is formed between the central convex portion and the first tube, between the central convex portion and the second tube, and between the central convex portion and the fin. Exchanger.
The heat exchanger according to claim 1, wherein the rib and the central convex portion are connected.
The heat exchanger according to claim 1 or 2, wherein the projection height of the rib and the projection height of the central convex portion are the same as each other.
Each said rib is
The storage medium container is formed to extend toward an end along the direction in which air passes in the cold storage material container, and the width along the vertical direction decreases as the end approaches the end. The heat exchanger according to any one of to 3.
When the space | interval along the up-down direction of a pair of said adjacent rib is made into an up-and-down space,
The heat exchanger according to claim 4, wherein the vertical distance at the position closest to the end is 1.5 or more times the vertical distance at the position closest to the center in the air flow direction.
The heat exchanger according to claim 4 or 5, wherein at least a part of the ribs extend in a downward direction toward the end.
The heat exchanger according to any one of claims 1 to 6, wherein a distance between the central convex portion and the tube is larger than a protruding height of the rib.
The heat exchanger according to any one of claims 1 to 7, wherein the central convex portion is formed to extend in the vertical direction.