JP2003336990A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compact heat exchanger having excellent pressure proofness. <P>SOLUTION: This heat exchanger 10 is formed by arranging first flow passages 2 and second flow passages 6 in different surfaces of a plate 3 working as a partition. Each first flow passage 2 is formed of a through-hole formed by punching a first flow passage plate 1 in the plate thickness direction, and the second flow passages 6 are formed between the second flow passage plate 5 and the partition plate 3. With this structure, fine flow passages having excellent pressure proof can be structured with a simple method using the through- holes provided in the flat plate as the first flow passages 2. Furthermore, a flat and wide heat transfer surface is formed by arranging these flow passages in a surface, and a thin heat exchanger can be structured. A compact heat exchanger having excellent pressure proofness is thereby provided. <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 more particularly, to a heat exchanger for refrigerant and water used in a water heater for generating hot water using a heat pump, a cooling / heating machine for generating cold / hot water, and the like. , A heat exchanger for transferring heat between different media.

[0002]

2. Description of the Related Art Conventionally, as this type of heat exchanger, a heat exchanger as disclosed in Japanese Utility Model Publication No. 62-5587 has been proposed. The configuration will be described with reference to FIG.

The heat exchanger 50 is used, for example, in a so-called heat pump water heater that heats the hot water by using the heat of condensation of the refrigerant, and the first heat transfer tube 51 through which the high temperature and high pressure refrigerant flows. And a second heat transfer tube 52 through which low-temperature low-pressure water flows, and the first and second heat transfer tubes 51 and 52 are provided.
Each is flattened and closely adhered to each other, and is spirally wound. At this time, the high-temperature refrigerant flowing through the first heat transfer pipe 51 exchanges heat with the low-temperature water flowing through the second heat transfer pipes 52 located above and below the first heat transfer pipe 51 to heat the water.

In the conventional example, the flatness is facilitated by using a thin tube body having a relatively small strength as the heat transfer tube, and the flattened area causes the tubes to adhere to each other, that is, the heat transfer area. The heat exchange performance is improved by enlarging.

[0005]

However, the above conventional structure has the following problems. For example, when the heat exchanger 50 is used as a heat exchanger having a very high operating pressure, for example, a carbon dioxide refrigerant and water, the pressure applied to the inside of the first heat transfer pipe 51 through which the high pressure refrigerant flows becomes very high. Therefore, in the conventional configuration in which the tubular body is mechanically flattened in advance, the tubular body is easily deformed and it is difficult to secure sufficient pressure resistance.

Further, as shown in FIG. 5, the heat exchanger 50 has a structure in which a first heat transfer tube 51 and a second heat transfer tube 52 are closely attached to each other and spirally wound to form a cylindrical heat. Since a dead space is formed inside the exchanger 50, the volume occupied by the heat exchanger is larger than the heat transfer area, and there is a problem that a large amount of space to store the heat is required inside the device.

The present invention solves the above-mentioned conventional problems and provides a compact heat exchanger having excellent pressure resistance.

[0008]

In order to solve the above-mentioned conventional problems, the heat exchanger according to the present invention has the first and second flow passages arranged on different surfaces of the plate serving as the partition wall, The flow path is formed by a through hole obtained by removing the first flow path plate in the plate thickness direction, and the second flow path is formed between the second flow path plate and the partition plate.

This makes it easy to form a fine flow path having excellent pressure resistance by a simple method of providing a through hole in the plate. Furthermore, by arranging such flow paths in a plane, it is possible to form a flat and wide heat transfer surface and configure a thin heat exchanger. Therefore, a compact heat exchanger having excellent pressure resistance can be provided.

[0010]

BEST MODE FOR CARRYING OUT THE INVENTION The invention according to claim 1 is characterized in that a first flow path and a second flow path are arranged on different surfaces of a plate serving as a partition wall, and the first flow path is a first flow path. The channel plate of 1 is formed by a through hole that is removed in the plate thickness direction, and the second channel is the second channel.
It is formed between the flow path plate and the partition plate, and it becomes easy to form a fine flow path excellent in pressure resistance by a simple method of providing a through hole in the plate. Furthermore, by arranging such a flow path in a plane, it becomes possible to form a flat heat transfer surface and configure a thin heat exchanger. Therefore, a compact heat exchanger having excellent pressure resistance can be provided.

According to a second aspect of the present invention, in addition to the configuration of the first aspect, in particular, a plurality of first flow paths are configured in parallel with each other, and a plurality of fine flow paths having excellent pressure resistance are provided. Moreover, by arranging them in parallel substantially in parallel, it is possible to form a flat and wider heat transfer surface. Therefore, it is possible to provide a heat exchanger having excellent pressure resistance, compact size, and excellent heat exchange performance.

According to a third aspect of the present invention, in addition to the configuration of the second aspect, a distribution flow passage communicating with a plurality of first flow passages is provided particularly in the partition plate, and has a simple configuration. The fluid can be easily distributed to the plurality of flow paths, and the heat exchanger can be made thin.

According to a fourth aspect of the present invention, in contrast to the configuration of the third aspect, particularly, the distribution channel has a substantially axisymmetric shape, and the fluid is evenly distributed to the plurality of first channels. It can be distributed, an effective heat transfer area is sufficiently secured, and high performance of the heat exchanger can be realized.

According to a fifth aspect of the present invention, in particular, the equivalent diameter of the distribution channel is larger than the equivalent diameter of the first channel. By making the pressure loss of the fluid in the first flow passage smaller than the pressure loss in the first flow passage, the fluid can be distributed more uniformly to the plurality of first flow passages, and the heat exchanger is further improved in performance. Can be realized.

According to a sixth aspect of the present invention, in addition to the configurations of the first to fifth aspects, the flow passage width of the second flow passage is formed to be larger than the flow passage width of the first flow passage. Yes, while the pressure resistance of the first flow path is improved by miniaturizing the flow path, the pressure loss of the fluid in the second flow path can be achieved without reducing the flow path width of the second flow path. Can be kept small. Therefore, it is possible to reduce the pressure loss on the second flow path side while maintaining the pressure resistance of the first flow path.

According to a seventh aspect of the present invention, in addition to the configurations of the first to sixth aspects, particularly, the first flow path and the second flow path are provided substantially all over the longitudinal direction thereof via the partition plate. Since they are formed at opposite positions, the fluid flowing through each flow path can perform heat exchange in the form of a counter flow with excellent heat exchange performance, thus achieving higher performance and compactness of the heat exchanger. it can.

According to an eighth aspect of the present invention, in addition to the configurations of the first to seventh aspects, particularly, the first flow path has a bent portion in the first flow path plate. By folding the flow path in the same plate surface, not only a linear flow path,
Since it is possible to configure a flow path having an arbitrary shape such as a rectangular shape or a spiral shape, it is possible to sufficiently reduce the length of the heat exchanger in the vertical direction or the horizontal direction even for a flow path having a long flow path length. A more compact heat exchanger can be realized.

The invention described in claim 9 is, in addition to the constitutions of claims 1 to 8, particularly on both surfaces with the first flow path interposed therebetween.
Since a plurality of second flow paths are provided through the partition plate, heat can be exchanged with the second flow path on both upper and lower surfaces of the first flow path, and a remarkably wide heat transfer area is secured. can do. Therefore, it is possible to provide a compact heat exchanger having excellent pressure resistance, high heat exchange performance, and high heat exchange performance.

The invention according to a tenth aspect is the first to ninth aspects.
In particular, the plate serving as the partition wall is composed of a plurality of plates in the plate thickness direction.
Even if an abnormality such as a crack occurs in the partition plate forming part of the flow channel or the second flow channel, the presence of the plurality of partition plates causes the fluid leaking from each flow channel to Since it is possible to prevent the heat exchanger from being mixed into the flow path, it is possible to improve the reliability of the heat exchanger.

The invention as defined in claim 11 is defined by claims 1 to 1.
In contrast to the configuration of 0, the flow passage height of the second flow passage is formed higher in the high temperature side passage than in the low temperature side passage. For example, when heating hot water or the like, scale is likely to occur particularly in the high temperature side passage near the outlet, but increasing the height of the passage at this portion alleviates clogging of the passage due to scale deposition, The life of the heat exchanger can be extended and the reliability can be improved.

[0021]

Embodiments of the present invention will be described below with reference to the drawings.

(Embodiment 1) FIG. 1 is a sectional view of a heat exchanger 10 of Embodiment 1 of the present invention, and FIG. 2 is a configuration diagram of the heat exchanger 10.

In FIG. 1, the heat exchanger 10 comprises a first flow path 2 and a second flow path 6 on different surfaces above and below the plate 3 serving as a partition wall. The first flow path plate 1 is formed by a through hole removed in the plate thickness direction, and the second flow path 6 is formed.
Is formed between the second flow path plate 5 and the partition plate 3. Specifically, the first flow path 2 is formed with a through hole in the flat plate-shaped first flow path plate 1 by, for example, punching or etching with a press machine,
The space is formed by sandwiching the partition plate 3 and the end plate 4 from both upper and lower sides. On the other hand, the second flow path 6 is a space formed by forming a groove in the second flow path plate 5 by, for example, drawing using a press machine and stacking the partition plate 3 and the second flow path plate 5 together. It is configured.

As shown in FIG. 2, a plurality of first flow paths 2 are arranged substantially in parallel with each other, and the second flow paths 6 are provided over the entire wall in the longitudinal direction via the partition plate 3. It is in the opposite position. In other words, the fluid A flowing in the first flow path 2 in the direction of the dotted arrow in the drawing and the fluid B flowing in the second flow path 6 in the direction of the solid arrow in the drawing are in counterflow. .

Further, inside the partition plate 3, there are provided distribution channels 13a and 13b which communicate with the respective channels of the first channel 2 when overlapped with the first channel plate 1. The distribution flow paths 13a and 13b have a substantially axisymmetric shape as shown in FIG. 2, and are symmetrical with respect to the streamline direction of the fluid A flowing through the first flow path 2.

The equivalent diameters of the distribution channels 13a and 13b are larger than the equivalent diameters of the channels of the first channel 2. This can be easily set by appropriately setting the height and width of each flow path. Further, as shown in FIG. 1, the flow passage width W2 of the second flow passage 6 is larger than the flow passage width W1 of the first flow passage 2.

The configuration of the inlet / outlet portion of each flow path is, for example, for the first flow path 2, the distribution flow paths 13a and 13a.
The second flow path plate 5 is provided with through holes 11a and 11b so as to communicate with 3b, and piping (not shown) is provided in these holes.
Is being planted. Further, with respect to the second flow channel 6, through holes 12a and 12b are provided in the second flow channel plate 5 so as to communicate with the second flow channel 6, and pipes (not shown) are provided in these holes. ) Is planted.

Here, examples of the material of the plate constituting the heat exchanger 10 include metals having good thermal conductivity and formability, such as copper, aluminum, and stainless steel. In addition, as a method of manufacturing the heat exchanger 10, brazing or integral joining by diffusion welding may be used.

The operation of the heat exchanger 10 configured as described above will be described below.

A high-pressure fluid is circulated in the first channel 2 and a low-pressure fluid is circulated in the second channel 6. If the heat exchanger 10 is used for a so-called heat pump water heater that heats the hot water by using the heat of condensation of the refrigerant, the high-pressure fluid is a refrigerant such as carbon dioxide, and the low-pressure fluid is hot water. Becomes At this time, the high-temperature, high-pressure refrigerant exchanges heat with the low-temperature, low-pressure water flowing through the second flow path 6 via the partition plate 3 while flowing through the first flow path 2.

According to the present embodiment, the flat plate-shaped first
A through hole is provided in the channel plate 1 of the first channel 2
It becomes easy to construct a fine flow path having excellent pressure resistance by a simple method of using Further, by arranging a plurality of such first flow paths 2 in parallel as shown in FIG. 2, a flat and wide heat transfer surface can be formed, and a thin and compact heat exchange surface can be formed. Can be provided.

Further, distribution channels 13a and 13b communicating with the plurality of first channels 2 are provided in the partition plate 3, and these are made to have an approximately axisymmetric shape, and further, their equivalent diameters are set to the first channels. The distribution channel 1 is made larger than the equivalent diameter of 2
By providing a difference in flow resistance between the first flow passage 2 and the flow passages 3a and 13b, it is possible to uniformly distribute the fluid to the plurality of first flow passages 2 and to effectively transfer heat over the entire heat transfer surface. The area can be secured.

Further, if the flow passage width of the second flow passage 6 is made larger than the flow passage width of the first flow passage 2, the pressure resistance of the first flow passage 2 is improved due to the miniaturization of the flow passage. On the other hand, it is possible to suppress the pressure loss of the fluid in the second flow channel 6 to a small level without particularly reducing the flow channel width of the second flow channel 6. This means that the pump power for transporting a fluid such as water to the second flow path 6 can be suppressed to a low level, and the second flow path 6 can be maintained while the pressure resistance of the first flow path 2 is maintained. It is possible to reduce the pressure loss on the side.

Further, the first flow path 2 and the second flow path 6 are
The fluids that are formed at positions facing each other across the partition plate 3 over substantially the entire lengthwise direction and that flow in the respective flow paths are in the form of a counter flow that excels in heat exchange performance as compared with parallel flow and cross flow. Therefore, the heat exchanger can be further improved in performance. Therefore, a compact heat exchanger having excellent pressure resistance, high heat exchange performance, and the like can be provided.

(Embodiment 2) FIG. 3 is a structural diagram of a heat exchanger 20 according to Embodiment 2 of the present invention. Embodiment 2 of the present invention is shown in FIG.
It has substantially the same structure as the heat exchanger 10 shown in FIG. The present embodiment is different from the first embodiment in that the first flow path 22 has a substantially U-shaped bent portion 28 within the surface of the first flow path plate 21. The first through the partition plate 23
The second flow path 26 is provided at a position facing the flow path 22 of the second flow path plate 25 and the partition plate 23 in which the groove is formed.
Is formed as a space between and, and also has a substantially U-shaped bent portion 29. The distribution channels 33a and 33b and the through holes 31a, 31b, 32a, and 32b have the same functions as those in the first embodiment, and thus the description thereof is omitted here.

By providing the first flow path 22 with a bent portion 28 having not only a substantially U shape but also a curved shape or an L shape, not only a linear flow path is formed on the first flow path plate 21. ,
It is possible to configure a flow path having an arbitrary shape such as a rectangular shape or a spiral shape. This means that the length of the heat exchanger 20 in the vertical direction or the horizontal direction can be made sufficiently small with respect to the flow path for which the flow path length needs to be extremely long according to the required heat transfer area. Therefore, with the above configuration, the heat exchanger can be made more compact.

(Third Embodiment) FIG. 4 is a sectional view of a heat exchanger 30 according to a third embodiment of the present invention. In FIG. 4, the heat exchanger 3
In the same manner as in the first embodiment, 0 has the first flow path 2 and the second flow path 6a arranged on different surfaces above and below the plate 3a serving as the partition wall, and the first flow path 2 is the first flow path. The flow channel plate 1 is formed by a through hole that is removed in the plate thickness direction, and the second flow channel 6a is formed between the second flow channel plate 5a and the partition plate 3a. In the present embodiment, further, on the lower surface of the first channel 2,
The second flow path 6b formed by the second flow path plate 5b is provided via the partition plate 3b.

The operation of the heat exchanger configured as described above will be described below.

For example, as described in the first embodiment, the first
Fluid of high temperature and high pressure in the flow passage 2 of the second flow passages 6a and 6b
It is assumed that the low-temperature and low-pressure fluids respectively flow into. At this time,
While flowing in the first flow path 2, the high-temperature high-pressure fluid exchanges heat with the low-temperature low-pressure fluid flowing in the upper and lower second flow paths 6a and 6b via the partition plates 3a and 3b. .

Here, according to the present embodiment, it is possible to exchange heat with the second flow path on both the upper and lower surfaces of the first flow path, and a remarkably wide heat transfer area can be secured. Further, if the low temperature side fluid is circulated in the second flow paths 6a and 6b,
The temperature difference from the atmosphere surrounding the heat exchanger is reduced, and the heat insulating property of the heat exchanger is also improved. Therefore, it is possible to provide a compact heat exchanger having excellent pressure resistance, high heat exchange performance and high heat exchange performance.

(Fourth Embodiment) FIG. 5 is a sectional view of a heat exchanger 40 according to a fourth embodiment of the present invention. Example 4 of the present invention is shown in FIG.
It has substantially the same configuration as the heat exchanger 20 shown in FIG. This embodiment is different from the first embodiment in that the plate 3 serving as a partition wall is composed of a plurality of plates 3a and 3b in the plate thickness direction and the flow path height of the second flow path 6 is The point is that the high temperature side channel 6d is formed higher than the low temperature side channel 6c. Here, in the production of the second flow paths 6 whose flow path heights are different on the way, grooves having different depths are partially formed in the second flow path plate 5 by using a method such as drawing. By doing so, it can be easily performed.

The operation of the heat exchanger 40 configured as described above will be described below.

In the first flow path 2, a high-temperature and high-pressure refrigerant such as carbon dioxide, hydrocarbon, and chlorofluorocarbon used in a heat pump device flows as the fluid A in the direction indicated by the dotted arrow in the drawing. It is assumed that low-temperature low-pressure hot water as the fluid B flows through the second flow path 6 in the direction indicated by the solid arrow in the figure. At this time, the high-temperature and high-pressure refrigerant flows through the partition walls 3a and 3b while flowing through the first flow path 2 and the second flow path 6 is formed.
It will exchange heat with the low temperature low pressure fluid flowing through it. The low-temperature low-pressure hot water is supplied to the outlet side of the second flow path 6 (the high temperature-side flow path 6).
In d), it becomes the highest temperature.

For example, the partition plate 3b forming a part of the first flow path 2 through which the high-temperature and high-pressure refrigerant flows is deteriorated or eroded over time due to corrosion or the like, and an abnormality such as a crack occurs on the inner surface of the partition plate 3b. Even when the refrigerant leaks from the first flow path 2 to the outside, the presence of the partition plate 3a causes the second flow path 6 to flow.
Since it is possible to prevent the inflow into the low-temperature low-pressure water, the high-temperature high-pressure refrigerant does not mix. Similarly, in the case where an abnormality such as a crack occurs in the partition plate 3a forming a part of the second flow path 6 through which the low-temperature low-pressure water flows, and the low-pressure water leaks from the second flow path 6 to the outside. However, since the partition plate 3b exists, the high-temperature and high-pressure refrigerant does not flow into the second flow path 6 through which the low-temperature and low-pressure water flows. At this time, the partition plate 3
If a minute groove communicating with the outer peripheral surface of these plates is formed between a and 3b, the leaked fluid can be discharged to the outside. Further, if a sensor corresponding to the fluid is installed, it is possible to detect the leakage of the fluid and detect the abnormality of the device.

Therefore, by forming a double partition structure between the respective flow paths, mixing of different fluids (for example, refrigerant and water) is prevented, so that, for example, the refrigerant of the heat pump device and the refrigerating machine oil serve as hot water. The risk of mixing can be reduced and the reliability of the heat exchanger can be improved.

In the case of a refrigerant-to-water heat exchanger that heats water (particularly tap water) with a refrigerant, generally, when water containing a large amount of hardness components such as calcium and magnesium is heated to a high temperature for a long period of time, it becomes the highest temperature. There is a possibility that scale is generated near the outlet of the water side flow path. If such a scale adheres to the inner circumference of the water-side flow path, it becomes a flow resistance of water and pressure loss increases, and the performance as a heat exchanger is reduced. Here, in this embodiment, since the flow path height of the high temperature side flow path 6d of the second flow path 6 is configured to be larger than the flow path height of the low temperature side flow path 6c, the water side should be provided. Even if scale is generated and adheres in the flow path, the increase in the flow resistance of water can be mitigated.

Therefore, for example, the blockage of the flow path due to scale deposition, which tends to occur particularly in the high temperature portion during heating of the hot water supply, is alleviated, the life of the heat exchanger is extended, and the reliability is improved.

[0048]

As described above, according to the invention described in claims 1 to 11, the first plate is formed on the different surfaces of the plate as the partition walls.
And a second flow path are arranged, the first flow path is formed by a through hole obtained by removing the first flow path plate in the plate thickness direction, and the second flow path is formed by the second flow path plate and the partition plate. It is easy to form a fine flow path with excellent pressure resistance by a simple method of forming a through hole in the plate. By arranging the heat exchangers in a flat shape, a flat and wide heat transfer surface can be formed, and a thin heat exchanger can be configured. Therefore, a compact heat exchanger having excellent pressure resistance can be provided.

[Brief description of drawings]

FIG. 1 is a sectional view of the same heat exchanger according to a first embodiment of the present invention.

FIG. 2 is a perspective view showing the configuration of the heat exchanger.

FIG. 3 is an exploded perspective view showing a configuration of a heat exchanger according to a second embodiment of the present invention.

FIG. 4 is a sectional view of a heat exchanger according to a third embodiment of the present invention.

FIG. 5 is a sectional view of a heat exchanger according to a fourth embodiment of the present invention.

FIG. 6 is a cross-sectional view of a conventional heat exchanger.

[Explanation of symbols] 1 First channel plate 2, 22 First channel 3 partition plates 5 Second channel plate 6, 6a, 6b, 26 Second flow path 6c Low temperature side flow path 6d High temperature side flow path 13a, 13b distribution channel 28 Bend

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Keijiro Kunimoto             1006 Kadoma, Kadoma-shi, Osaka Matsushita Electric             Sangyo Co., Ltd. (72) Inventor Ryuta Kondo             1006 Kadoma, Kadoma-shi, Osaka Matsushita Electric             Sangyo Co., Ltd. (72) Inventor Satoshi Imabayashi             1006 Kadoma, Kadoma-shi, Osaka Matsushita Electric             Sangyo Co., Ltd. (72) Inventor Koji Oka             1006 Kadoma, Kadoma-shi, Osaka Matsushita Electric             Sangyo Co., Ltd. F-term (reference) 3L065 DA12                 3L103 AA05 AA50 BB43 DD15 DD55

Claims (11)

[Claims] 1. A first flow path and a second flow path are arranged on different surfaces of a partition plate serving as a partition, and the first flow path includes the first flow path plate in the plate thickness direction. A heat exchanger, which is formed by a removed through hole and in which the second flow path is formed between a second flow path plate and the partition plate. 2. The heat exchanger according to claim 1, wherein a plurality of first flow paths are arranged in parallel. 3. The heat exchanger according to claim 2, wherein the partition plate is provided with a distribution flow path communicating with the plurality of first flow paths. 4. The heat exchanger according to claim 3, wherein the distribution channel has a substantially axisymmetric shape. 5. The heat exchanger according to claim 3, wherein the distribution channel has an equivalent diameter larger than that of the first channel. 6. The heat exchanger according to claim 1, wherein the flow passage width of the second flow passage is formed larger than the flow passage width of the first flow passage. 7. The first flow path and the second flow path are formed in substantially the entire lengthwise direction thereof and at positions facing each other through a partition plate, and the fluid flowing through each flow path is defined as a counter flow. The heat exchanger according to any one of claims 1 to 6. 8. The heat exchanger according to claim 1, wherein the first flow path has a bent portion in the first flow path plate. 9. The heat exchange according to claim 1, wherein a plurality of second flow paths are provided on both surfaces of the first flow path with a partition plate interposed therebetween. vessel. 10. The heat exchanger according to claim 1, wherein the plate serving as the partition wall is composed of a plurality of plates in the plate thickness direction. 11. The heat exchanger according to claim 1, wherein the flow passage height of the second flow passage is formed higher in the high temperature side flow passage than in the low temperature side flow passage.