JPS5929992A - Stacked type heat exchanger - Google Patents

Abstract

PURPOSE:To obtain the stacked type heat exchanger having a large heat exchanging capacity by a method wherein the flow speeds of both heat exchanging liquids are increased and both of the liquids are flowed opposingly along the whole of the flowing paths thereof. CONSTITUTION:The blade-tube side liquid enters from an inlet pipeline 4 and the stream thereof is branched before entering into the layer-type flowing paths 8. The flow directions of the liquids in each layer-type flow paths are turned twice by bulkheads 12, 13, thereafter, are joined together to discharge them through an outlet pipeline 5. On the other hand, cylinder side liquid enters from the inlet pipeline 6 into the layer-type flow path 9, exchanges the heat thereof with tube plate side liquid while turning the flow direction twice by the bulkheads 14, 15 in the manner of the opposing flow, thereafter, it is joined together and is discharged from the outlet pipeline 7. In this case, the flow speed of both liquids becomes substantially three times as compared with the conventional stacked type heat exchanger and, therefore, a large heat exchanging capacity may be obtained. In case of a single phase flowing, for example, the heat transfer rate is made proportional to the flow speed to the power of 0.8 generally in case of a turbulent flow, therefore, the heat transfer rate of about 2.4 times of the conventional stacking type heat exchanger may be obtained in both liquids. Further, a large temperature efficiency may be obtained because all heat exchanging flow paths are formed into meandering flow paths of counter-flow type.

Description

[Detailed description of the invention] The present invention relates to a stacked heat exchanger.

A conventional stratified heat exchanger will be explained with reference to FIGS. 1 to 3. In Figures 1 to 3, 1.2 is a heat exchanger shell, 3 is a plate tube, 4 and 5 are inlet piping and outlet piping for fluid on the plate tube side, respectively, and 6 and 7 are inlet piping for fluid on the body side, respectively. and outlet piping, 8 is a laminar flow path on the plate tube side, and 9 is a laminar flow path on the shell side. Each plate tube has an entire flow path formed by joining the outer peripheries of two plates, and vibrators 10, 111C, l:, ! at the inlet and outlet portions of the flow path, respectively. l) Joined with other plate tubes. The plate tube side fluid flows in from the inlet pipe 4, separates, passes through the laminar flow path 8, joins together, and flows out from the outlet pipe 5.

The body side fluid flows in from the inlet pipe 6 and is divided into a laminar flow path 9.
While passing through the plate tube side fluid, the fluid exchanges heat with the fluid on the plate tube side in a counter-flow manner, then merges and flows out from the outlet pipe 7. Such a heat exchanger is disclosed in, for example, Japanese Utility Model Application No. 48-4457.

Generally, an effective method to obtain the maximum heat exchange capacity is to increase the flow velocity of both fluids to increase the total heat transfer coefficient. However, in conventional laminated heat exchangers, the flow velocity of both fluids is determined by the cross-sectional area of each laminar flow path, so the flow velocity cannot be increased arbitrarily, so it is difficult to improve the heat transfer coefficient. It has the disadvantage that it cannot be used.

An object of the present invention is to provide a stacked heat exchanger with a large heat exchange capacity by simultaneously increasing the flow speeds of the side heat exchange fluids and making both fluids flow in opposite directions throughout the flow paths.

In order to achieve the above object, the present invention forms all the heat exchange channels of both laminar channels into meandering channels with counterflow, thereby increasing the flow rate of the side heat exchange fluid at the same time, and improving the heat exchange capacity. It was designed so that

An embodiment of the present invention will be described below with reference to FIGS. 4 to 8. In this example, each fluid changes direction twice in the same valley layered flow path. In FIGS. 4 to 8, parts that are the same as or similar to those in FIGS. 1 to 3 are indicated by the same reference numerals, and their explanations are given in gold foil. Reference numerals 12 and 13 indicate partition walls of the flow passages on the plate tube side, and 14 and 15 indicate partition walls of the flow passages on the body side, which have an L-shape. It is placed inside the flow path.

Next, the operation of this embodiment will be explained. The fluid on the brate tube side flows in from the inlet pipe 4 and is divided into the laminar flow path 8
to go into. In each layered channel, there are partition walls 12 as shown in FIG.
, 13, and then merge and exit from the outlet pipe 5. On the other hand, the body-side fluid flows in from the inlet pipe 6, branches off, and enters the laminar flow path 9. In each laminar flow path, as shown in Figure 8, the direction is changed twice by the partition walls 14 and 15, and after exchanging heat in a counter-flow with the fluid on the plate tube side, the fluid merges and exits through the outlet pipe 7. In this embodiment, the flow rate of both fluids is approximately three times that of the conventional stacked heat exchanger shown in FIGS. 1 to 3, resulting in a large heat exchange capacity. For example, in the case of single-phase flow, the heat transfer coefficient is generally proportional to the 0.8th power of the flow velocity in the case of turbulent flow, so for both fluids it is approximately 2.4 times that of the conventional stacked heat exchanger shown in Figures 1 to 3. In addition, since the total heat exchange flow path is a meandering flow path with counterflow, a large temperature efficiency can be obtained. In addition, although the above-described case is a case in which both fluids change direction twice in each laminar flow path, and the flow velocity is approximately tripled, the present invention is not limited to this example; The shape, number, arrangement, etc. of the partition walls may be completely changed so that the flow velocity of the partition walls is set to the required magnitude and heat exchange is performed in counterflow within the entire flow path.

FIG. 9 shows another embodiment in which protrusions 1G, 17, 17a and 17b'i are formed on a plate tube to form a meandering flow path. 3 is the plate tube,
The protruding portion 16 is a protruding portion that constitutes a partition wall of the laminar flow path on the plate tube side, and the height of the protrusion is the same as the flow path surface height Hl, and the protrusion portions 17, 17a, and 17b constitute the partition wall of the layered flow path on the body side. In the protrusion, the width of the protrusion 17 is H2, and the protrusion depth of the protrusions 17a and 17b is 1 (forming 8 channels. Fig. 10 shows still another embodiment. 16c, 1).
6d is a protrusion that constitutes a partition wall of the plate tube side laminar flow path, and 17a, 17b, 17c, and 17d are protrusion portions that constitute a partition wall of the body side laminar flow path. This ability (according to the Ip example, the protrusions 16c, 1 (3d,
The height of the protrusions 17c and 17d can be lowered, making it easier to apply.

As described above, according to the present invention, the flow rate of the side heat exchange fluid can be increased arbitrarily at the same time to completely increase the heat transfer coefficient.Furthermore, counterflow heat exchange can be performed over the entire flow path, so that the maximum heat can be achieved. A stacked heat exchanger with exchange capability can be obtained.

[Brief explanation of drawings]

Figure 1 is a plan view of a conventional stacked heat exchanger, Figure 2 is a gP
, FIG. 3 is a longitudinal sectional view taken along line 8-A in FIG. 1,
FIG. 4 is a plan view showing one embodiment of the present invention, and FIG.
6 is a sectional view taken along the line B-B in FIG. 4, FIG. 7 is a sectional view taken along line C-C in FIG. 5, FIG. FIG. 10 is a perspective view of another embodiment, and FIG. 10 is a perspective view of still another embodiment. 1.2... Heat exchanger body, 3... Plate tube,
J, 2, 13... Partition wall of plate tube side laminar flow path, 14° 15... Partition wall of body side laminar flow path, 16, 1
6c, 16d... protrusion, 17, 17a,
17b, 17c, 17d---protrusions. Representative Patent Attorney Tadashi Akimoto Figure 1 Figure 2 Figure 4 Figure 5 Figure 6 Figure 7 Figure 9 Figure 10 Figure 16 (1bO procedural amendment (voluntary) Patent dated July 29, 1982 Director-General Kazuo Wakasugi 1, Indication of the case 1988 Patent Application 1n/3ri7/ta No. 2, Title of the invention Laminated heat exchanger 3, Amendment person 71 [Relation with the case H patent applicant Address: 5-7 Marunouchi-chome, Chiyoda-ku, Tokyo Name (510) Hitachi, Ltd. 4, Agent Figure 5 Figure 6 IO14B

Claims (1)

[Claims] 1. A plate duplex that completely forms a laminar flow path through which a heat exchange fluid flows is provided in the heat exchanger body, and the heat exchanger body and the plate tube have a layered space between the other heat exchanger. A laminated heat exchanger for circulating an exchange fluid, characterized in that the total heat exchange passages of both laminar passages are meandering passages with counterflow. 2. FiIj layered thermographic heat exchanger according to claim 1, in which the meandering passages are formed by an even number of passages. Claim 2, in which the six meandering passages are formed by a plate tube and a partition wall separate from the body. A laminated heat exchanger according to scope 1. 4. The laminated heat exchanger according to claim 3, wherein the partition walls are members formed in an r, Nr-type. 5. The laminated heat exchanger according to claim 1, wherein the meandering flow path is formed by a protrusion formed on the plate tube. 6. The laminated heat exchanger according to claim 5, wherein the plate tubes are entirely formed with protrusions on both sides, and their tips abut against each other to form partition walls.