HEAT EXCHANGER FOR COOLING TOWER

Abstract: The heat exchanger has a zig-zagged liquid-flowing passage (14) and an overflowed-liquid escaping conduit (17). When an excessive amount of cooling water is supplied to the heat exchanger, a part of cooling water flows into the overflowed-liquid escaping conduit (17) through a dam (16) formed between the liquid-flowing passage (14) and the escaping conduit (17). The heat exchanger is formed by assembling a plurality of heat exchanging partition plates (11) formed by molding, which have the same shape and the same dimensions, and which are easily engageable with and detachable form each other.

Description: The present invention relates to a heat exchanger, particularly, it relates to an indirect contact type heat exchanger for a cooling tower with features according to the preamble of Claim 1. Such an exchanger is known from DE-A-26 02 679. An indirect contact type heat exchanger for a cooling tower is widely used as a closed type heat exchanger or such a type of heat exchangers that it is mounted on a packing material consisting of a large number of corrugated plates in a parallel arrangement to prevent generation of whitish smoke or mist. An example of the inner structure of the heat exchanger is shown in Figures 24 to 26 in which air passages for feeding air in the horizontal direction are separated by metallic plates or synthetic resin plates from liquid-flowing passages for feeding liquid in the vertical direction so that the two kinds of passages are arranged alternately. Heat-exchanging efficiency is increased by reducing the space of the liquid-flowing passages as possible. In each of the liquid-flowing passages, there are formed a number of deflectors projecting from the partition plates in the liquid-flowing passages to reduce a flow speed of the liquid to thereby further increase heat-exchanging efficiency. The corresponding Japanese Unexamined Patent Publication No. 100370/1976 to the above mentioned DE-A-2602679 discloses a heat exchanger for cooling tower which comprises a plurality of thin, flat liquid-flowing passages arranged vertically and in parallel to each other and a plurality of thin, flat air-flowing passages extending vertically which are alternately interposed between the adjacent liquid-flowing passages, wherein each of the liquid-flowing passages is separated from each of the air-flowing passages by a heat exchanging partition plate made of a synthetic resin so that the liquid and air are fed in the passages in a non-contact state. Both walls for forming of each of the air-flowing passages are formed by an inverse U-shaped member. The adjacent inverse U-shaped members are connected to each other by means of ribs projecting from the side walls so that a liquid-flowing passage is formed between the connected inverse U-shaped members. The heat exchanger disclosed in the above-mentioned publication is mounted on a cooling tower by hanging a plurality of the inverse U-shaped members above the packing material held in the cooling tower by means of a horizontal supporting beam as shown in Figure 27, or it is mounted on a cooling tower by hanging a plurality of vertically arranged heat exchangers inside the packing material which is disposed at an outer air inlet port of the cooling tower as shown in Figure 28. This arrangement of the heat exchangers is to prevent generation of white smoke or mist in the winter season. In the conventional heat exchangers, however, there is such a disadvantage that when it is used for a long time, dust or microorganisms deposit on the wall surface of the liquid-flowing passages which are generally narrow and are curved in order to reduce the falling speed of the liquid flowing by the action of gravity. As a result, the optimum flow rate of liquid can not be obtained, and there often causes flooding of the liquid at the liquid supplying side of the heat exchanger. This results in not only wetting the heat exchanger but also reduction of an amount of a refrigerant circulated in the heat exchanger. In a case that the heat exchanger is used for a cooling tower by disposing it above the packing material to disperse the liquid discharged from the heat exchanger onto the packing material, the quantity of the dispersed liquid (water) becomes short to thereby invite the shortage of liquid circulating in the cooling tower. In such a type of cooling tower that a plurality of the heat exchangers are supported by hanging them in a multi-stage at the inside of the packing material which is disposed at the outer air inlet port of the cooling tower (Figure 28), the shortage of the liquid in the cooling tower results in the generation of whitish smoke or mist. It is an object of the present invention to provide an indirect contact type heat exchanger for cooling tower or a heat exchanger unit as the major component of the heat exchanger which has a simple structure and is capable of maintaining the optimum flowing rate of liquid even when there causes clogging in a part of the heat exchanger or the heat exchanger unit. This object is solved according to the invention by a heat exchanger in accordance with the patent claim. The invention is more fully described with reference to the accompanying drawings, in which: Figure 1 is a longitudinal cross-sectional view of a first embodiment of the heat exchanger according to the present invention; Figure 2 is a sectional view taken along a line 2-2 in Figure 1; Figure 3 is a perspective view partly broken of a second embodiment of the heat exchanger according to the present invention; Figure 4 is a front view showing a modified form of the second embodiment of the present invention; Figure 5 is a cross-sectional view taken along a line 3-3 in Figure 3; Figure 6 is a cross-sectional view taken along a line 4-4 in Figure 3; Figure 7 is a sectional view taken along a line 5-5 in Figure 3; Figure 8 is a cross-sectional view partly broken of a modified form of the second embodiment showing the lower part of the heat exchanger; Figure 9 is a front view partly broken of a third heat exchanger without the overflow being shown; Figure 10 is a front view partly omitted of a similar heat exchanger in that shown in Figure 9; Figure 11 is a front view partly broken of a third embodiment according to the present invention; Figures 12 through 16 are respectively cross-sectional views taken along lines 4-4, 5-5, 6-6, 7-7, and 8-8 in Figure 9; Figure 17 is a bottom view partly omitted of the heat exchanger shown in Figure 9; Figure 18 is a front view partly broken of a sixth embodiment or the heat exchanger according to the present invention; Figures 19 through 23 are respectively cross-sectional views of the heat exchanger unit taken along lines 4-4, 5-5, 6-6, 7-7, and 8-8 in Figure 18; Figure 24 is a schematic view showing a conventional heat exchanger; Figure 25 shows the conventional heat exchanger from the front part; Figure 26 is a diagram showing another conventional heat exchanger; and Figures 27 and 28 are respectively diagrams showing conventional heat exchangers used for a cooling tower to prevent the generation of whitish smoke or mist. Figrues 1 and 2 show a first embodiment of the heat exchanger. In Figures 1 and 2, a number of inverse U-shaped partition plates 11 made of a good heat conduction material such as copper, aluminum and so on are disposed in a generally rectangular casing 10 in a parallel arrangement with a slight gap (about 3 mm - 5 mm) between the adjacent partition plates. The inner part of each of the inverse U-shaped partition plates is not closed by the wall surface of the casing, whereby there is provided air-flowing passages 12 for feeding air in the horizontal direction. The top of each curved portion 13 of the inverse U-shaped partition plates 11 is determined to be lower than the upper edge of the casing 10. Liquid-flowing passages 14 are respectively formed by providing a slight gap between the adjacent partition plates 11. An upper liquid storing portion 15 is formed in the casing 10 in a portion above the curved portion 13 of the partition plates 11. Each of the liqud-flowing passages 14 is separated by a dam 16 which vertically extends in the casing at a position near an outer wall of it, from a vertically extending overflowed-liquid escaping conduit 17. The liquid-flowing passages 14 constitute a liquid-falling speed reducing part 18. The liquid-falling speed reducing part 18 has curved flow-passages 20 by means of a number of deflectors 19 projecting from the partition plates 11 toward the liquid-flowing passages 14. In the embodiment shown in Figure 1, a zig-zagged curved passage 20 is formed by the deflectors 19 projecting from one side wall 21 of the casing 10 and the dam 16 opposing to the side wall 21 in a manner of alternately projecting in the horizontal direction from the upper part to the lower part of the casing 11. The upper and lower ends of the casing may be opened. However, when a top plate 22 and a bottom plate 23 are respectively provided, a liquid supplying port 24 and a discharge port 25 are respectively provided at a part of the top plate and the bottom plate. In this case, the overflowed-liquid escaping conduit 17 and the liquid-falling speed reducing part 18 are respectively communicated with the common liquid supplying port 24 at the upper part and the common discharge port 25 at the lower part. The function of the first embodiment will be described. When cooling water as a refrigerant which is warmed by a load such as an air conditioner or a refrigerator (at a temperature of 30°C-70°C) is supplied from the top of the casing 10 to the liquid-falling speed reducing part 18, the cooling water gradually falls in the curved passages 20 defined by the deflectors 19 while it is sufficiently agitated between the partition plates 11. While the cooling water falls in the curved passages 20, it contacts the partition plates 11 in a longer time than a case when it falls straightly, whereby heat exchanging is effected between the cooling water and air flowing in the horizontal direction in each of the tunnel-like air-flowing passages 12; thus the cooling water is cooled. If a flow rate of cooling water becomes irregular, or the flow rate is temporally increased, or the sectional area of the liquid-falling speed reducing part 18 becomes narrow due to deposition of microorganisms on the wall of the part 18, there causes reduction in the flow rate 17. In this case, when the water level in the liquid storing portion 15 rises to exceed the height of the dam 16, a part of cooling water overflowed flows in the overflowed-escaping conduit 17 to be directly discharged from the casing. Accordingly, there is no danger of flooding of water to wet around the heat exchanger. Also, an irregular supply of the cooling water circulated in the cooling tower and the heat exchanger can be avoided. Figure 3 shows a second embodiment of the heat exchanger. A reference numeral 30 designates a heat exchanger unit having a thin, flat hollow body formed by a vacuum-molding method or a blow-molding method of a synthetic resin such as polyvinyl chloride, polyethylene, polypropylene and so on. The thickness of the wall of the heat exchanger unit is preferably in a range of from 150 µm to 500 µm. The size of the heat exchanger unit is preferably 40 cm - 90 cm wide, 50 cm - 150 cm long and 3 mm - 5 mm thick in inside span; however, these dimensions are not critical. The heat exchanger unit 30 is provided with a liquid supplying port 31 at the upper part and a discharge port 32 at the lower part. A groove 33 is formed in the liquid supplying port 31 so as to extend vertically from its top end to the lower part whereby the groove reaches the inner cavity of the heat exchanger unit 30. The groove 33 functions as an air communicating part. The air communicating part 33 may be formed in the upper part of the heat exchanger unit 30 so as to be independent of the liquid supplying port 30. The heat exchanger unit 30 formed by using a vacuum-molding method has a peripheral sealing part 36 formed by melt-bonding the circumferential parts of two wall plates 34, 35 and a sectioning sealing part 39 which is in parallel to the side edges 37, 38 of the heat exchanger unit 30 and is slightly inside the one side edge 37 and which is formed by melt-bonding enlongated ridges extending along the side edge 37 in the both wall plates 34, 35. The upper and lower ends of the sectioning sealing part 39 terminate respectively near the upper and lower edges 40, 41 of the heat exchanger unit 30, but they do not reach the edges 40, 41. A number of deflectors 42 are formed in the horizontal direction on both the wall plates 34, 35 in the area between the sectioning sealing part 39 and the other side edge 38. The positions of the deflectors formed on the one wall plate 34 are made alternate to those of the deflectors on the other wall plate 35 when the both wall plates 34, 35 are assembled, whereby a liquid-flowing passage in a zig-zagged form is provided in association with the sectioning sealing part 39 and the other edge 38 in the hollow portion of the heat exchanger unit 30, thereby obtaining a liquid-falling speed reducing part 44. The areas of the both wall plates 34, 35 corresponding to the liquid-falling reducing part 44 constitute the major heat exchanging surface of the heat exchanger unit 30. A narrow vertical section defined by the sectioning sealing part 39 and the side edge 37 provides an overflowed-liquid escaping conduit 45. The upper edge 46 of the sectioning sealing part 39 functions as a dam. The position of the uppermost deflector 42 is determined to be slightly lower than the upper edge 46 of the sectioning sealing part 39. Thus, the liquid-falling speed reducing part 44 is defined by arranging the deflectors 42 so as to extend horizontally and alternately from the sectioning sealing part 39 and the other side edge 38 as shown in Figure 3. However, the arrangement of the deflectors 42 may be such that as shown in Figure 4, a number of short deflectors are formed in each of the wall plates 34, 35 without positional relationship between the deflectors of the both wall plates. In this case, the liquid-falling speed reducing part 44 is so formed that a large variety of liquid-flowing passages 43 are provided in the heat exchanger unit 30. There are at least two hanging means, e.g. two holes 47 in this embodiment at the upper edge 40 of the heat exchanger unit 30. Figure 7 shows a modified embodiment of the heat exchanger unit 30. A number of projections and recesses 49 are formed on the both wall plates 34, 35 in the areas corresponding to the liquid-flowing passages. At least one projection 29 is formed in the peripheral sealing part 36 of each of the wall plates 34, 35 at the positions corresponding to each other. The heat exchanger unit may be formed by the vacuum-molding method or the blow-molding method. The projection 29 functions as a spacer for maintaining the inner space of the heat exchanger unit 30 which is formed by assembling the both wall plates 34, 35. During the operation of a cooling tower with the heat exchanger units 30 described above, the liquid supplying port 31 of each of the heat exchanger units 30 is communicated with the atmosphere through the air communicating groove 33, whereby cooling water flows through the zig-zagged liquid-flowing passage or passages due to the gravity. The cooling water in the heat exchanger unit is entirely discharged due to the atmospheric pressure when the operation of the cooling tower is stopped. Since the small projections and recesses 49 are formed in the wall plates 34, 35, there is obtainable a greater heat-transferring surface area to thereby further improve heat-transferring efficiency. Since the projection or the projections 29 are formed in the peripheral sealing parts 36 of the wall plates 34, 35 so as to use them as the spacers, assembling work of a number of the heat exchanger units 30 can be easy, and it is unnecessary to prepare additional or separate spacers. The air communicating groove 33 formed at a part or the liquid supplying port 31 makes the structure of the upper part of the unit simple and can be formed at the same time of molding the heat exchanger unit by the vacuum-molding method or the blow-molding method. Further, the manufacturing cost of the unit is relatively low. By using the blow-molding method, the heat exchanger unit can be obtained without forming the peripheral sealing part 36. Accordingly, the appearance of the heat exchanger unit becomes good and a broader heat-exchanging surface area can be obtained. A plurality of discharge ports 32a may be formed at the lower part of the heat exchanger unit 30 as shown in Figure 8. Figures 9, 10 and Figures 12 through 17, which show heat exchangers without the overflow part. The overflow for these heat exchangers is shown in Fig. 11. In Figure 9 a symbol A shows as a whole a heat exchanger for a cooling tower. The heat ecxchanger A is provided with a plurality of thin, flat liquid-flowing passages 50 arranged in the vertical direction and in parallel to each other, and a plurality of thin, flat air-flowing passages 51 interposed between adjacent two liquid-flowing passages 50 of the plurality of liquid-flowing passages 50, wherein a plurality of heat exchanging partition plates 52 are interposed between the adjacent liquid-flowing passage 51 and the air-flowing passage 50 to provide a partition to render the two kinds of fluids to be in a non-contact state. The two adjacently placed heat exchanging partition plates 52, which constitutes walls for a single air-flowing passage 51, form a single heat exchanger unit B by connecting the upper edges of the plates in their entire width direction. A plurality of the heat exchanger units B are arranged in a single and same casing C in parallel to each other to form each liquid-flowing passage 50 between each adjacently placed two heat exchanger units B. The heat exchanger A is constituted by arranging the plurality of heat exchanger units B so that they are engageable with and detachable from each other at the planes where the liquid-flowing passages are formed. Each of the heat exchanging partition plates 52 is formed by a molding method so as to have the same size and the same dimensions. The heat exchanger unit B is formed by opposing a couple of the heat exchanging partition plates 52, i.e. one being reversed, followed by connecting their upper edges. The heat exchanging partition plate 52 has a number of deflectors 54 in an expanded form at the area except the edge portions. Namely, the deflectors 54 are distributed in a discrete and alternate manner in the horizontal and vertical direction in the partition plate 52. The heat exchanger units B are assembled in such a manner that the deflectors 54 projecting from a first heat exchanger unit B are fitted to recesses formed in a second heat exchanger unit B while the deflectors projecting from the second heat exchanger unit extend toward the first heat exchanger unit, whereby a zig-zagged liquid-flowing passages is formed between the first and second heat exchanger units B. The deflectors 54 will be explained in more detail. Referring to Figures 12 through 16. Of the two adjacent heat exchanging plates 52 to form a liquid-flowing passage 50 therebetween, the tip of each of the deflectors 54 of the heat exchanging plate 52 of the first heat exchanger unit B is fitted into each corresponding shallow recess formed in the heat exchanging partition plate 52 of the second heat exchanger unit B, while the tip of each of the deflectors 54 formed on the heat exchanging partition plate 52 of the second heat exchanging unit B is fitted into each corresponding sharrow recess formed in the heat exchanging partition plate of the first heat exchanger unit B. Thus, the deflectors 54 functions not only to provide curved liquid-flowing passages but also to provide spacers for the liquid-flowing passages defined by the first and second heat exchanger units B. The distance of the liquid-flowing passages 50 defined by the two heat exchanger units B is in a range from 2 mm - 5 mm, preferably, about 2 mm. The thickness of the partition plate 52 is in a range from 0.2 mm to 0.4 mm. At both side portions of each of the heat exchanging partition plates 52, a plurality of stripe-like projections and recesses 55 are formed over the entire length. These stripe-like projections and recesses 55 provide sealing portions at both side areas 50a, 50b of the zig-zagged liquid-flowing passages 50 by the mutual engagement of the projections and the recesses 55 when the heat exchanger is assembled (Figure 17). At least one engageable and detachable notch or fastener may be provided at a part of the stripe-like projections and recesses 55 to secure the engagement of the projections and recesses 55, if necessary. A modification of the heat exchanger of Fig. 9 will be described with reference to Figure 10. In Figure 10, the same reference numerals as in Figure 9 designate the same or corresponding parts and therefore, description of these parts is omitted. The lower edge 56 of the heat exchanger unit B is integrally connected over its entire width, whereby there is provided a heat exchanger A1 for cooling tower in which air-flowing passages are closed at their upper and lower ends; the upper parts of the passages are connected to a common liquid supplying port; and their lower parts are connected to a common discharge port. We will now describe the overflow which has been omitted from Figures 9 and 10 for reasons of simplicity. For the third embodiment of the heat exchanger we will refer to Figure 11. In Figure 11, the same reference numerals designate the same or corresponding parts a in Figure 9, and therefore, description of these parts is omitted. In the third embodiment a heat exchanger A2 for cooling tower has a liquid-flowing passage section 50A which comprises in general a liquid-falling speed reducing part E in the central area, overflowed-liquid escaping conduit parts F at both sides of the liquid-falling speed reducing part E and stripe-like projections and recesses 59 provided between the liquid-falling speed reducing part E and the overflowed-liquid escaping conduit parts F. The liquid-falling speed reducing part E is formed by a number of the deflectors 54 in the heat exchanging partition plate 52 in the same manner as in Fig. 9. A plurality of the heat exchanger units B comprising a couple of the heat exchanging partition plates 52 are assembled by mutually fitting the deflectors 54 in the recesses formed in the heat exchanging partition plates 52. The liquid-falling speed reducing part E is separated from the overflowed-liquid escaping conduit parts F by the vertically extending stripe-like projections and grooves 59. The upper edges of the stripe-like projections and recesses 59 extend to the upper part of the heat exchanger unit B to form dams G for liquid overflowed, whereby when cooling water is excessively supplied to the heat exchanger, a part of cooling water escapes through the conduit parts F. Reference numerals 55 designates sealing parts at both edges of the heat exchanger and the sealing means may be in a form of the stripe-like projections and grooves. In the third embodiment each of the heat exchanging partition plates 52 has the same size and the the same dimensions. Accordingly, it is easily manufactured by a molding method. Further, in storage and transportation of the heat exchaing partition plates before assembling work, they are not bulky and save a space. When the heat exchanging partition plates 52 are assembled to form to heat exchanger units B, assembling working can be easy by simply opposing a couple of the partition plates 52, followed by connecting their upper edges 53. Figures 18 through 23 show modified versions of the third embodiments as shown in Figures 9 through 17 whereby again the oberflow part has been omitted for simplicity sake. In the Figures the same reference num designate the same or corresponding parts. A number of expanded projections 60 are formed in each of the heat exchanging partition plates 52 at same positions. The expanded projections 60 function as spacers for air-flowing passages 51 when a couple of the heat exchanging partition plates 52 are assembled to form a heat exchanger unit B. Each of the expanded projections 60 may take a shape of cone 62 with a bottom 61 opened and a flat apex portion. The inner surface 62 of the conical-shaped expanded projection 60 functions as a vortex-flow-generating means in the liquid-flowing passages. Of the a couple of the heat exchanging partition plates 52 constituting a single heat exchanger unit B, a small projection 64 is formed in the top surface of each of the expanded projections 60 of the first heat exchanging partition plate 52. On the other hand a small recess 65 is formed in the top surface of each of the expanded projections 60 of the second heat exchanging partition plate 52. Thus, position adjustment of the first and second heat exchanging partition plates 52 is effected. It is clear that the above-mentioned structure can also be applied to the structures shown in Figures 10 and 11. In the heat exchangers described with reference to Figures 18 through 22, the danger of deposition of dust or microorganisms can be reduced because vortex flows are resulted due to the vortex-flow-generating means when the cooling water flows in the liquid-flowig passages. Further, by engaging the small projections and the small recesses, accurate positioning of the heat exchanger unit in an assembled heat exchanger can be obtained. In the heat exchanger shown in Figures 9 through 22, the upper edge portion 52a of each of the heat exchanging partition plates 52 may be bent to the same side as the expanded projections 53 into an L shape so that it is flush with the top of the expanded projections 53. In this case, a single heat exchanger unit B is formed by facing a couple of the heat exchanging partition plates 52 in which one of the partition plates 52 is reversed and by connecting the upper edges 52a along there entire width. In this case, the projections 53 of both the heat exchanging partition plates 52 are mutually met so that air-flowing passages having a constant distance can be realized by the spacing function of the projections 53. The heat exchanger A is assembled by the thus formed heat exchanger units B as follows. A plurality of the heat exchanger units B are disposed in parallel to each other in a casing C; the stripe-like projections and recesses 55 of a heat exchanging partition plate 52 of one heat exchanger unit B are engaged with those of an adjacent heat exchanger unit B to form a liquid-flowing passage part having sealing portions at both sides of it; engagement of these stripe-projections and recesses 55 are carried out for the other heat exchanger units successively; and a liquid supplying port is formed at the upper edges 52a of the heat exchanging partition plates 52 so as to be communicated with the liquid-flowing passages. In this case, each of the heat exchanger units B are connected at the plane for forming liquid-flowing passages so as to be freely engageable and detachable. When the heat exchanger is used for a cooling tower in the condition as shown in Figure 27, i.e. the heat exchanger is disposed on the packing material, the cooling water is cooled in the heat exchanger by indirect contact with air passing therethrough and it is dispersed on the packing material. Then, the cooling water is brought in direct contact with air to be cooled. On the other hand, the temperature and the humidity of the air are increased, and the air is forced toward the outlet where it is mixed with air which has an elevated temperature but the same absolute humidity as the atmosphere, whereby the mixed air is discharged out the cooling tower without generating whitish smoke or mist. When the heat exchanger is used for a cooling tower under the condition as shown in Figure 28, i.e. the heat exchangers are disposed in multi-stage inside the packing material, air having an elevated temperature and a high humidity is fed to the heat exchanger through the packing material in which the air is brought in direct contact with the cooling water. On the other hand, the cooling water falling through the zig-zagged liquid-flowing passages in the heat exchanger gradually enters into the lower heat exchangers during which heat exchanging is effected between the air and the cooling water, whereby the air having an elevated temperature is discharged out the cooling tower without causing whitish smoke or mist. Even when an excessive amount of cooling water is supplied to the heat exchanger by any cause such as clogging in a part of liquid-flowing passages, a part of cooling water is escaped through the overflowed-liquid escaping conduit to be discharged outside the heat exchanger. Therefore, a continuous operation can be attained without limiting an amount of cooling water to be supplied to the heat exchanger.

Claims: A heat exchanger for cooling tower comprising a plurality of heat exchanging partition plates 11 made of metallic plates or synthetic resin plates arranged to form a plurality of thin, flat liquid-flowing passages 14 and a plurality of thin, flat air-flowing passages 12 which are alternately interposed between the adjacent liquid-flowing passages, so as not to have air contact with liquid passed therethrough; and defectors 19 are arranged on the surface of each of said partition plates 11 in the direction of its width so as to project toward said liquid-flowing passages to thereby form a liquid-falling speed reducing part 18, characterized in that a vertically extending overflowed-liquid escaping conduit 17 is formed adjacent said liquid-falling speed reducing part by means of a dam 16.

Inventors: KASHIWADA, KEN SHINWA SANGYO CO., LTD., MUTO, TADANOBU, SASAKI, TETSUO SHINWA SANGYO CO., LTD.
Applicants: SHINWA SANGYO CO., LTD.
Application year: 1988
Main classification: F28C1
IPC codes: F28C1, F28F21, F28D9, F28B1