JPH07504264A - heat exchanger assembly - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed description of the invention] heat exchanger assembly field of invention This invention relates to an improved heat exchanger core, and more particularly, to an improved heat exchanger core in which thermal energy is transferred to one side. Multiple heat exchanger elements or or a heat exchanger core that combines modules.

Background technology There are many types of heat exchangers known in the art. These are roughly two main groups. It can be divided into The first group is cylindrical tube heat exchangers, and the second group is cylindrical tube heat exchangers. is a plate heat exchanger. An example of a cylindrical tube heat exchanger is a tube heat exchanger that includes a row or bundle of tubes and an external and a surround for the membrane. A plate heat exchanger is described in US Pat. No. 4.282. 927, or a plate fin structure as described in U.S. Patent No. 4.823.8. 2 or more when the plates are stacked together in a hermetically sealed manner as described in 67 It has a rectangular laminated plate that creates a flow path from the fluid.

In each of the above two groups, a number of parts are made to manufacture the heat exchanger. and combined with each other. In a cylindrical tube heat exchanger, for example, several The tubes are assembled into bundles and the ends of the tubes are sealed into corresponding openings in a pair of tubesheets. Preferably, baffles are installed along the length of the bundle. Then a bundle of tubes, The baffle plate and tubesheet are arranged at a pair of ends around the tubesheet so that two flow paths are formed. placed in a pressure vessel that seals the The first flow path is around the outside of the tube and between the tubesheets; A second flow path exists inside the tube and within the end chamber of the pressure vessel. Cylindrical structure and plate structure In both heat exchangers, a large amount of material is provided to form and seal the fluid flow paths. Since the flow path is formed by assembled parts, one fluid can flow into the other. There is always a risk of leakage into the fluid.

In addition, the assembled heat exchanger is free of welds, seams or adjacent parts of this heat exchanger. Ineffectiveness caused by multiple boundaries formed by parts connecting elements suffer from damage. The above boundary is the resistance to heat transfer to the heat transfer surfaces of this exchanger. Grant area. Heat exchangers formed by processes such as extrusion or casting The integral part of the is known as the "primary structure" and is welded or Must be distinguished from otherwise attached elements. including boundaries Elements such as are called "second-order" structures. Similarly, the surface of a primary structure is a "primary" table A surface of a "secondary" structure is known as a "secondary" surface.

The above drawback is that when heat exchange from liquid to air is required through a plate heat exchanger, Particularly harmful. Air cooling media lead to inherent inefficiencies in prior art heat exchangers. The generally low heat capacity of the body is relatively low compared to the respective liquid and cooling or hot air flows. This always results in a larger exchanger being required.

Reference is made to US Pat. No. 3,202,212, which constitutes an example of the prior art. This details The document refers to heat exchange elements made of extruded aluminum. this heat The exchange element has a plurality of first fluid passages provided in the body portion thereof, and a plurality of first fluid passages provided in the body portion thereof. It has many spiny projections extending outward from its wide surface. Each barb is , were thin and relatively small in cross section. It has the maximum heat transfer effect from the main body. This is to provide a high ratio of exposed surface to the mass of the barbs in order to achieve a . However, each barb may include several to form separate rows of , so that horizontal grooves are formed between adjacent rows. , were separated from each other. Also, vertical grooves are formed, so that this heat exchanger shaped to facilitate possible cross-flow of the second fluid relative to the parallel flow of the first fluid. It had been done. This structure allows a cross-flow of the second fluid to remove and dissipate heat at a desired rate. was not as effective as a parallel flow system to provide a given heat transfer efficiency I didn't. This means that cross-flow heat exchange systems are not connected to external water pipes like parallel flow systems. This happens because it is not suitable. Also, parallel flow systems become more compact and therefore more efficient construction in terms of being more suitable for laminated or modular construction. achieve.

This is especially true for engines used in vehicles or stationary applications. This is also true for heat exchangers used in air conditioners.

Also, the continuation of the initial extrusion (in the process, the Formed by cutting or gouging barbs from precursor ribs The barbs added to the material sub- sequently add to the manufacturing cost of the heat exchanger. The process of gouging was inefficient.

Also, Australian specification 85777/75 and US specification 4.565. See 244. These specifications are similar to U.S. Specification 3.202.212. A heat exchanger with a structure and further challenges to the above-mentioned drawbacks are presented.

Also, similar to U.S. Patent 3.467, 190, U.S. Patent 3.743.252; ．． 352.008; 3.566, 959: 4, 567, 074; 3.137. See 785. All of these are useful background prior art in connection with this invention. mentioned. These citations indicate that the configuration of the extruded monolithic product is not new; Additionally, U.S. Patent No. 3,137,785 has a body with vertically extending fins on each side. Showing a monolithic extrusion for use as an element of an electric heater with a body There is. There are multiple extruded channels within the body. However, these for receiving or containing a tubular heating element or a temperature sensitive control element. It is not a flow path.

U.S. Patent No. 3.566,959 as a heat sink in semiconductor silice Concerns aluminum extrusions for applications.

U.S. Pat. It is mentioned plainly. It has a tubular body and integrally projects radially from this tubular body. It has some interior and exterior fins. However, this reference cannot be considered to be related to the invention of

Reference is also made to UK patent 2142129. This includes a rectangular elongated hollow body. A radiator formed from the above is described. The hollow body has, on each of its two sides, A plurality of spaced apart heat dissipating fins are provided. between adjacent fins It is located so as to form multiple air paths. Multiple open end diameters with the above fins A cover plate for forming a channel extends across the outer ends of each set of fins. .

Heat transfer from hot fluid flowing through an elongated hollow body through its open-ended path allows air to be heated by the

This reference indicates a parallel flow condition and therefore in relation to U.S. Patent 3.202.212. Although cross-flow aluminum extrusions can solve the problems discussed above, there are operational issues. The problem still occurred. The air flowing through the adjacent tips of the heat exchanger fins is The air having qualitatively the same temperature and flowing through the base area of each air path of the heat exchanger Such extrusions are fundamentally inefficient in operation because of their different temperatures. This is due to the fact that there is. In this regard, the adjacent fins of the heat exchanger The substantially cooler air passes through the base area of each air path of the heat exchanger than the substantially cooler air passes through the tip of the heat exchanger. It will be appreciated that the air flowing through the air is substantially hot or at an elevated temperature. Dew.

This is because the base region of each channel is located immediately adjacent to the elongated hollow body. This is because the tip of the fin is located substantially far away from the elongated hollow body. .

Therefore, the efficiency of this heat exchanger, which requires a uniform heat transfer coefficient, is The hottest part of the heat exchanger is located at the base area of each passage, and the hottest part of the heat exchanger is located at the base area of each passage. Thermal gradients resulting from the location of the desired portion adjacent to the tip of the fin will be harmed by In addition, this problem of lack of heat exchange efficiency is caused by This is because the amount of air passing through the fins is greater than the amount of air passing through the base area of the air path. And it will get worse.

Heat exchanger similar to radiator as described in U.S. Patent 4.341.346 Refer to the vessel. It has a central tubular duct for the passage of hot water and this central tubular duct. It has a pair of webs that extend on either side of the duct. The fins located opposite each other are Located on each side of the web and extending perpendicular thereto. British patent 2142129 The conclusions expressed above in connection also apply to this prior art reference. similar conclusion is US Patent 3.147.802, UK Patent 1.411.162 and US Patent This also applies to 4.296.539.

U.S. Patent No. 4.401.155 describes a heat exchanger composed of multiple laminated modules. related.

Each module has a closed path for high pressure flow and vertically above and/or from this path. Or have fins that extend downward. The fins allow the modules to run parallel to each other. When stacked along their length, they form an open path suitable for low pressure flow. each The fins are of uniform thickness and have the same dimensions perpendicular to the above path. It is noteworthy that there are Each module is a single aluminum extrusion throughout It consists of The heat exchanger of U.S. Pat. No. 4.401.155 is particularly suitable for high pressure applications, Particularly intended for cases where one heat exchange stream is at high pressure and the other heat exchange stream is at low pressure. It is.

This is particularly relevant for low temperature generation processes.

In U.S. Pat. No. 4.401.155, the first embodiment (i.e. FIGS. 1.3 and 4) Regarding this, there are as many paths as there are fins. is attracting attention. On the other hand, in another second embodiment (i.e. Figures 2.6.7 and 8) Two paths are provided for each fin.

In the first embodiment, the heat exchanger device has a path surface area that is substantially the same as a fin surface area. Since it is the same, it is not efficient in terms of effective heat transfer. In this regard, by As discussed in detail, for effective heat transfer to occur, the surface area of the fins must be It was determined that the surface area of the tract should be substantially larger than the surface area of the tract. This thing is , the density of one fluid (e.g. air) passing through the fins is higher than that of the fluid passing through the above path. This is important in situations where the density of water (e.g. water) is significantly different.

In this situation, air has a much lower density than water, which means that air has a much lower density than water. This means that it also has a very small effective heat storage capacity. Therefore, this means that Effective heat transfer from the water path through the heat exchanger walls to the fins is determined by the surface area of the fins. This means that this occurs only when the surface area of the path is significantly larger than the surface area of the path. This is A large surface area of the fins should be passed through the heat exchanger wall from the above path to the fins. This occurs to facilitate heat absorption. Thereby, such heat is transferred through the fins. transmitted to the passing air. At the same time, the air is It must be able to absorb heat satisfactorily from the fins. In this regard, through the fins The amount of air passing through should be in significant excess over the amount of water passing through the above path. Ru.

With respect to the second embodiment mentioned above, such an embodiment proposes the following structure. I don't serve it. i.e., thereby a heat exchanger formed from a series of stacked modules. Uniform heat transfer with respect to the core extends outward from at least the peripheral module does not provide structure such as that obtained with relationships involving fins. This is a US patent 3.202.212 formed from the extrudates discussed in detail above with respect to It's also a problem with the heat exchanger core. However, U.S. Patent No. 4,401,155 It is interesting to note that the description of the laminated structure of the roll is relevant. Thereby, The outward facing fins from one module form an interleaved structure (, Extending into the channels formed by adjacent fins of the module. similar A stacked structure with an interstitial array is shown in US Pat. No. 3,476,179. And the United States The same conclusion expressed here in connection with the first embodiment of patent 4401155 is The same applies to references.

Also, it is shown in German patent 3011011 and Japanese patent 55-152397. The heat exchanger described above is substantially as described above in connection with U.S. Pat. No. 4,401,155. It is believed that it does not provide efficient heat transfer for the same reason.

Additionally, heat exchangers formed as extruded monoliths with multiple fins are Therefore, U.S. Patent No. 3.202.212, Aus. Tralia national patent 85777/75, US patent 4.565.244; 3.743 ．． 252:4.352.008;3.566,959;4.567K References such as 074; 3.137.785 and 3.467, 180 also prone to these drawbacks.

See also US Pat. No. 5,042,247. This is a half-half with dissimilar properties. Two junctions are created as a result of conductive materials being connected electrically in series and thermally in parallel. Regarding thermoelectric coolers. The semiconductor materials mentioned above are of N and P type. Typical In thermoelectric coolers (TECs), these alternating columns of N-type and P-type semiconductor materials serve as conductors. It has an end connected to a winding wind by an electric body. these conductors is a metal coating typically formed on an insulating or ceramic plate. child When a direct current is passed through the TEC, the heat is absorbed by the cold steel ceramic and the semiconductor material and is dissipated on the temperature control ceramic. Dissipates heat from the TEC to the surrounding environment To achieve this, a heat sink must be attached to the temperature-regulating ceramic. Hee Without a sink, the TEC will overheat and fail within seconds.

In fact, a heatsink is used by a TEC or computer so that the heat is quickly dissipated. Typically attached to machinery or equipment that produces a substantial amount of heat, such as a computer. It is a device that allows Therefore, the heat sink dissipates heat at a greater rate It is more forward motion. Therefore, U.S. Patent 5.042.257 for TEC A heat sink is listed. This heat sink has a pair of opposing plates. These plates have a plurality of fins on each of the opposing surfaces. fins on one side One row of fins is rested or interposed between the other row of fins on the other side. Ru. Thereby, one row of fins has a thermal surface area contact for sufficient heat exchange. the desired position by suitable holding means such as a pair of relatively short fins forming the can be held. However, the heat sink was designed for proactive use. The relevant factors that must be taken into account when designing a heat exchanger are When a designer considers parameters, it will be recognized that they are not related. this This is especially true for the channels and channels for the two fluids flowing in a heat exchange relationship through the core. This applies to the design of a heat exchanger core with a stacked array of heat exchanger modules with .

Additionally, research into heat sinks is being carried out through associated conduits to achieve maximum heat exchange efficiency. It will be recognized that this is a considerable departure from other heat exchanger studies, which include the requirements for

Therefore, a heat exchanger that is relatively efficient and can reduce the problems of the prior art mentioned above. It is an object of the present invention to provide a device.

The heat exchanger device of the present invention comprises a plurality of first fluid zones and a plurality of second fluid zones. together, each first fluid zone is adjacent to and substantially in contact with each second fluid zone. Heat exchanger assembly formed from a primary structure consisting of cores arranged parallel to each other wherein each of the first fluid zones is closed by a peripheral wall, while each of the second fluid zones is closed by a peripheral wall; The body region includes a first fin extending from one of the peripheral walls adjacent the first fluid region. a second column extending from another of said peripheral walls adjacent said first fluid zone; a row of fins, and each of the first fins has a row of adjacent second fins. extending in a gap arrangement across the fins and having a surface area of each of said second fluid zones; It is characterized by a surface area that is substantially larger than the surface area of one fluid section.

Preferably, the first fluid zone is provided with a plurality of webs. Each web has a pair of peripheral walls extending from opposite surfaces, thereby providing a plurality of parallel first fluid paths. this web serves for augmentation and strengthening purposes to maintain the structural integrity of the core mouth The tip of the first row of fins is connected to another of the peripheral walls adjacent to the first fluid region. Conveniently adjacent or attached to an adjacent surface. As a variant, the first fi More preferably, the tips of the rows of holes are spaced apart from the other adjacent surface.

Similarly, the tip of the second row of fins is located at one of the peripheral walls adjacent to the first fluid zone. adjacent to or attached to two adjacent surfaces, but spaced apart from this one adjacent surface. It is more desirable to

Naturally, the tips of the first and/or second row of fins are for the second fluid when adjacent to or attached to the mating surface of the surrounding wall It will be appreciated that separate flow paths may be provided. first fin and/or or if the tips of the second row of fins are spaced apart from the adjacent surface of the combined peripheral wall; and each second fluid section may correspond to a single flow path for the second fluid.

one-piece, such as an extrusion formed from aluminum or other suitable metal It is within the scope of the present invention to provide a heat exchanger core that can be formed. However However, it is preferred that the core is formed from a plurality of separate modules. special The module includes a flow path for a first fluid and a first fin and a second fin. Advantageously, it has a peripheral wall delimiting both rows. The above fins are Extending away from the exterior or outer surface of the opposing portion of the circumferential wall.

The peripheral wall and elongated fins of each module are extruded or cast simultaneously. As a result, the heat exchanger module is formed from a primary structure. This is an important feature of the present invention. In other words, secondary structures that can lead to the drawbacks discussed above does not exist at all. In addition, the first fluid path and the second fluid path are as described above. Virtually similar to form a parallel flow heat exchanger core with the advantages of cross flow heat exchangers are parallel to each other. These benefits include:

(i) Since the second fluid consists of a cooling medium such as air, the parallel flow structure to facilitate conduiting the air to and removing air from the heat exchanger core. this When the fan pulls air through the heat exchanger and removes hot air from the heat exchanger, Can be used to leave. This means that the heat exchanger core of the present invention can be used, for example, in an automobile. When used as a radiator, there is no need to rely on atmospheric air to pass through. It means no. Therefore, the heat exchanger core of the present invention is placed at the front of the vehicle. There is no need to

(ii) When used as a radiator, the heat exchanger core of the present invention There is no need to have large flat surfaces as required with radiators.

This heat exchanger core can therefore be designed in a very compact shape. This means that In the case of trucks, the shape of the vehicle may be modified to allow reducing wind resistance. or increase the use of interior space in the case of large buses and buses. It means to do something.

(iii) Conduiting hot air from the heat exchanger core of the present invention Facilitates the use of hot air for other purposes such as supply or power source.

(iv) Since the fluid paths are parallel, this means that the heat exchanger element of the present invention is This means that it can be manufactured as an integral molded product. Extrusion molded products have a cross-flow structure. cannot be produced satisfactorily. Also, this means that the fin Rather than having parts wrinkled, welded or soldered, the heat exchanger of the present invention means forming an integral part of the converter core.

Avoiding this secondary structure maximizes heat transfer from fluids to be cooled by other fluids. Make it bigger.

(v) As a result of (iv) above, the extruded integrally molded product is cut to the desired length. and to other heat exchanger elements or modules to produce the core of the invention. and can be removably attached.

(νi) The heat exchanger core of the present invention is much more efficient and lighter than conventional products. stomach.

It is powered by a main power source (e.g. engine or motor) for operational purposes. I don't really ask for much.

The core of this heat exchanger device is defined by the given definitions for scheme 1 and 2nd fluid flow. It can take any shape that matches the function of . For example, a core is a continuous The target cross section may be provided with flow channels arranged in the direction of the indefinite length.

Such structures have been found to be particularly amenable to continuous casting or extrusion.

The perimeter wall of each module is for applications joined by a pair of opposing vertical sections. It is preferably substantially rectangular with a pair of substantially horizontal portions.

Said web of the first fluid zone formed by the circumferential wall is substantially in said vertical section. It is preferable that they be parallel to each other.

However, the peripheral wall can also have any shape in cross-section, such as circular, triangular, polygonal. It will be appreciated that other suitable shapes may also be had. first fluid in first fluid zone The path can take any suitable shape or configuration, including round in cross section.

It may be rectangular or polygonal.

The structure of the fluid path or fluid paths described above may depend on the application of the heat exchanger. It will be recognized and recognized that much depends on the material of manufacture of the heat exchanger core. cormorant.

Also, the elongate fins can take any suitable shape. however, This is not absolutely important, but each fin has a constant height and width. It is preferable. And, although this is not absolutely important, each elongated frame Preferably, the fins have, for example, a constant height and width. And, for example, each detail Long fins may be used if the heat exchanger element of the invention is produced as a casting. may taper in width from one end to the other. Elongated fins cover their surface have protrusions or protrusions on the outer surface if desired to increase the Also good.

Also, if it is considered appropriate, an internal It is also within the scope of the invention to have fins.

The heat exchanger core of the present invention includes a first and a second fluid, respectively, to their respective fluid zones. Manifold means adapted to supply may be provided. Such a maniho The holding means can take any suitable shape. Then, the first fluid one fluid zone, and a second fluid zone, a second fluid zone; An inlet manifold and an outlet manifold may be provided. As a variant, minutes Separated first and second fluid manifolds provide an inlet and an outlet. may be provided.

However, the inlet and outlet of the first fluid and the second fluid to the core are orthogonal to each other. It is preferable to have a suitable manifold hand to achieve this purpose. It is preferable to choose tiers.

Therefore, in this regard, the flow of the first and second fluids through their respective manifolds will be normal to each other, but this is not essential; each manifold The field is such that the first fluid and/or the second fluid are in the respective core inflow directions and the core It can also be configured to flow at an acute angle to the outflow direction.

Suitably, the first fluid is a "fluid to be manipulated", and is a fluid to be manipulated. is treated by a heat exchanger and is suitable for applying the heat exchanger of the present invention. refers to something that can be circulated through a flow path system. Such fluids can be used, for example, in vehicles. For radiators, water is suitable.

Suitably, said second fluid is an "active fluid", said active fluid being It acts as a refrigerant for the fluid being processed, and also acts as a refrigerant for the fluid being operated as it passes through the heat exchanger core. absorbs heat from the fluid produced. Such fluids can be used, for example, in vehicle radiators. In this case, compressed air is suitable.

However, the above is not essential, and the "active fluid" according to the present invention is , can become the "operated fluid" if necessary.

The heat exchange module used in the present invention can be installed vertically or horizontally, if necessary. Vine adapted to stacking. In particular, each module has a coupling means for this purpose. can be provided. In a preferred embodiment of the invention, said connecting means comprises adjacent The connections between the modules should be such that they define a suitable flow path for the second fluid. can be done.

Preferably, each module is such that adjacent modules of the invention are not assembled together. It has an integrally extruded connecting means to enable it to be connected. The above connection means may be of any suitable type, e.g. female member or socket. May be a male member or protrusion capable of snap-fitting or interference-fitting can. Each module connects the corresponding top or bottom of the adjacent module Suitably includes top and bottom connecting members that can fit into the members.

Said top or bottom connecting member is preferably connected to the bearer of the adjacent module. mating with a corresponding ratchet rib or flange on the top or bottom connecting member. Consists of vine-like ribs or flanges.

of modules or heat exchange elements used in horizontal or vertical stacking arrangements. The number depends individually on the desired application.

The heat exchanger core according to the present invention can be used for gas/gas, liquid/gas, liquid/liquid It can also be used in applications, especially those using compressed ambient air as the heat transfer fluid. Suitable for gas/air and liquid/air applications. Alternatively, a heat exchanger The core may be placed in an enclosure suitable for natural or ventilated air convection. can. Of course, water, ethylene glycol, ammonia and fluorinated hydrocarbon compounds, Heat transfer fluids other than air can also be employed, such as silicon compounds, mineral oil, etc.

If the above flow path is a series manifold, the flow of the first fluid is directed to the heat transfer fluid. As countercurrent flow, you get the largest log-average temperature difference between both fluids for the most efficient heat transfer. It is preferable to obtain Alternatively, the first fluid or heat transfer fluid may rise to a sudden temperature. If you are sensitive to changes or have upper or lower temperature limits, you can use co-current flow. Wear.

The material of the heat exchanger core of the present invention may be any suitable material; The properties are usually determined in relation to the conditions of application to which the material is placed. For example, extreme high When used in high-temperature applications, ceramic materials are specified because of their high-temperature properties. On the other hand, aluminum or its alloys are suitable for low temperature applications. I understand. Because these materials have a relatively high thermal conductivity, This is because the wall thickness per unit ratio may be large and therefore the mechanical strength can be increased.

Brief description of the drawing Reference will now be made to preferred embodiments of the invention as illustrated in the accompanying drawings. here in, Figure 1 shows a heat exchanger assembled by stacking four modules according to the present invention. FIG. 3 is an end view of the core of FIG.

FIG. 2 is a similar view of the core shown in FIG. 1 with the peripheral fins removed.

FIG. 3 is a perspective view of a heat exchanger module made in accordance with the present invention.

FIG. 4 shows the structure of FIG. 2 assembled in accordance with the invention and having a suitable manifold It is a figure showing a heat exchange device using a core.

FIG. 5 is a diagram showing a heat exchanger assembly of the present invention used in a vehicle engine. Ru.

Figure 6 shows the temperature distribution of the fins and the space between the fins when in use. FIG. 3 is a detailed diagram of the module.

BEST WAY FOR CARRYING OUT THE INVENTION FIG. 1 shows a heat exchanger according to the invention comprising a vertical stack of modules 11. Core is shown. Each module 11 has a peripheral wall 12 with a shallow rectangular contour. However, said profile has opposing horizontal portions 13 and opposing vertical portions 14 . continuous Said layer W12 delimits a first fluid zone 15. Separated first channel 17 A web 16 is provided.

Additionally, a first row of fins 18 extending from one horizontal portion 13 of the peripheral wall 12 and A second row of fins 19 is provided extending from the opposite horizontal portion 13.

The area 20 for the flow path of the second fluid therefore extends from between adjacent fins 19. and are separated by fins 18 which terminate near the horizontal portion 13 of the peripheral wall 12. , which limits the space 21 and extends from between adjacent fins 18 to form a peripheral wall 12. space 21 bounded by fins 19 terminating near the horizontal portion 13 of the limit. Spaces 22 are also shown between adjacent fins 18 or 19.

Each adjacent module 11 has a vertical extension 25 of the vertical portion 14 at the end of each peripheral wall 12. It is attached by a rib 23 of the module that fits with the tip 24 of the module a.

The effective flow path of the heat exchanger core 10 includes a first fluid zone 15 and a second fluid zone 17. It is important to realize that Therefore, in the area between dashed lines AA and BB A duct or manifold connects the fluid sections 15 and 17.

This, of course, applies to the outer circumferential fins 18a and 198 regarding the heat exchanger 10 of the present invention. means that it has no function and can be omitted or removed. Same thing, outside The same can be said of the circumferential extension portion 25a. This indicates that the heat exchange device of the present invention is effective. This means that the core is shown in FIG. The rib 23a can also be omitted. can. FIG. 2 thus defines a core 10a assembled according to the invention. do.

Of course, this does not mean that the core 10 cannot be used. Ko It is better to use A10a for heat exchange that also integrates appropriate inlet and outlet manifolds. It is more convenient because it saves space and storage capacity within the organ system.

FIG. 3 shows the diagram of the individual modules for the core 10.10a shown in FIG. A perspective view is shown. Each of the fins 18 and 19 has a thin cross-section outer periphery 18b and 19. b.

FIG. 4 shows a heat exchange device according to the invention, which includes an inlet 2 Gas or air inlet duct or inlet manifold 27 with 8 and FIG. A core 10a consisting of five modules 11 assembled as shown in 2 and an outlet 29 a gas or air outlet duct or outlet manifold 28 with fins 18; a gas or air section 20 containing and 19; a liquid section 15; and an air or gas section 19. A welding area 32 of the liquid area 15 which functions as a stopper or lid to prevent entry into and exit from the area 20. , a liquid inlet manifold 33 with inlet pipes 34, 35, 36, 37 and an attached outlet. and a liquid outlet manifold 38 with mouth tubes 39,40,41,42.

Each of the inlet manifolds 33 has an inlet slot 34b (i.e., there are two slots). ), 35b, 36b, and 37b, the respective compartments 34a, 35a, and 36a , 37a. Similarly, the outlet manifolds 38 each have outlet slots 39b ( That is, there are two slots), and the respective compartments 39a aligned with 40b, 41b, and 42b. , 40a, 41a, and 42a.

In the modified example of the heat exchange device shown in FIG. 4, a pair of air manifolds are provided at both ends of the core 10a. It turns out that there is no need to use field 27. In other words, 1 near the entrance end of the core 10a ; one manifold 27 is used to supply air (e.g. an air blower or air compressor); (by machine) to force the flow to flow through the core 10a, or alternatively, to force the flow to flow through the core 10a. Using only one manifold 27 near the mouth end, air is drawn into the core 10 by an exhaust fan. It is possible to allow the flow to flow through a.

The heat exchange device 26 is used for gas and liquid heat transfer. like this In typical equipment, the gas inlet and outlet manifolds are located on opposite sides of the core. Located at the end, the liquid inlet manifold and outlet manifold are on the same side.

placed on different sides or on the top and/or bottom of the core if appropriate. It is preferable that Therefore, the gas has one path through the core, and the liquid also has one path through the core. It will form a path that runs through A. If the same fluid is being processed, each master of the fluid The nifold has a single inlet and a single outlet, allowing different liquids to pass through the core 10a. In case of processing, it has different inlet and outlet as shown in FIG. Thus When the core 10a is used in a vehicle, for example, the inlet pipe 34 is connected to the engine cooling water. The inlet pipe 35 is for engine oil, the inlet pipe 36 is for gear oil, and the inlet pipe 37 is for air. Each is used for harmonic condensate. Conduits 39, 40, 41, 42 as outlet pipes has similar functionality.

In Figure 5 a reference is shown for a truck or vehicle 63, in this figure an engine Fuel from line 64 passes through line 65 to a heat exchanger assembly constructed in accordance with the present invention. The flow passes through the assembly 66. A fuel tank 67 can be used, and this fuel tank is , the fuel is returned to the engine 64 via line 68.

From the above discussion of the preferred embodiments shown in FIGS. The advantageously constructed heat exchanger core overcomes the disadvantages already mentioned in the prior art. Because F Illustrated arrangement of heat exchanger cores, i.e. conventional heat exchanger cores, typically also cold The tips of the fins 18 and 19 are the hottest parts of the conventional heat exchanger core. By being placed very close to a certain peripheral wall 12, heat distribution is uniform throughout the core. This is because cloth can be obtained. Therefore, the temperature of the core at the tip of the fin 1.8.19 is Of course, the temperature is substantially the same as or slightly lower than the temperature of the peripheral wall 12. It becomes. This means that a uniform heat distribution or uniform temperature distribution is obtained in each liquid zone. This means that this results in significantly improved heat exchanger efficiency. heat Exchanger efficiency is based on the core 10 or 10a being a single piece aluminum extrusion. or alternatively a stack of 10 aluminum extrusion modules or This can also be improved by making it as 10a.

The above-mentioned effect is illustrated in Figure 6, which shows the individual fins 18,19 and their The temperature distribution over the nearby space 22a is shown in relation to a conventional heat exchanger.

Figure 11 By adopting the gap arrangement structure as shown in Figure 2, the hot area becomes the cold area. This results in a uniform heat distribution or uniform temperature distribution as described above. You will find that it is possible.

From the above, the heat exchange device of the present invention has a function as a radiator for a vehicle. This is most useful for the gas-to-gas or liquid-to-liquid processes mentioned above. It will also be appreciated that this does not preclude its use as a heat exchanger. Peripheral wall 12 and the vertical extension 25 are preferably the same and, for example, approximately three or more thick. Lower, more convenient (such as less than 2m11 or l, 5+u or 1.ha) Sea urchin is relatively thin.

The surface area of the second fluid zone 20 is preferably at least the surface area of the first fluid zone 15. is also twice as large, more conveniently at least seven times as large.

The spaces 21 are substantially uniform, which means that the spaces 21 between adjacent fins 18,19 The same can be said about 2. Naturally, each first flow path 17 has substantially the same volume.

<a:1' -N RG, 3 1G, 5 Temperature according to Mr. Jen scale 77.5° - 76,5° field strength ■※green drowning 7], 5° -70,5'76.5° -75,5°5 Aoguchi Ineyuen■7o,5°-695°75.5°-74-5°ro ==Kosui-ku Suizan69.5°-68,5°74.5'-73,5°■Soba□Yoro■ Shock country 68.5° - 67,5° 73.50 - 72.5° Shiji Shiji Shijiji decoy rooster = mouth 67.5 °-66,5' Request for submission of translation of written amendment (Article 184-8 of the Patent Law) August 2, 1994 90 liters

Claims (14)

[Claims] 1. Consisting of a large number of first fluid zones and a plurality of second fluid zones, each first fluid zone a region disposed adjacent to and substantially parallel to each second fluid region; In a heat exchanger assembly formed from a primary structure consisting of a core, each of the first The fluid zones are closed off by a peripheral wall, while each said second fluid zone is connected to said first flow zone. a first row of fins extending from one of the peripheral walls adjacent the body area; a second row of fins extending from another of the peripheral walls adjacent the body area. In addition, each of the first fins has a gap arrangement between each adjacent second fin. and the surface area of each of the second fluid zones is greater than the surface area of each of the first fluid zones. A heat exchanger assembly characterized in that the size of the heat exchanger is substantially larger. 2. 2. The heat exchanger assembly of claim 1, wherein each of said first fluid zones comprises an upper A heat exchanger comprising one or more webs extending from opposite sides of a circumferential wall. converter assembly. 3. The heat exchanger assembly of claim 1, wherein the first row of fins comprises: spaced apart from another adjacent surface of the circumferential wall adjacent the first fluid region; A heat exchanger assembly characterized in that the heat exchanger assembly has a free end or tip, respectively. 4. The heat exchanger assembly of claim 1, wherein the second row of fins comprises: spaced from an adjacent surface of one of the peripheral walls adjacent to the first fluid zone; A heat exchanger assembly characterized in that it has a free end or tip, respectively. 5. The heat exchanger assembly of claim 1, wherein the core comprises a plurality of modules. each module includes the peripheral wall, the first row of fins, and the first row of fins. A heat exchanger assembly comprising two rows of fins. 6. 6. The heat exchanger assembly of claim 5, wherein the peripheral wall of each module is , a heat exchanger assembly characterized in that it is substantially rectangular. 7. The heat exchanger assembly of claim 1, wherein the first fluid zone and the first a manifold adapted to supply a first fluid and a second fluid to two fluid zones, respectively; a first fluid inlet and an outlet for the core; A heat exchanger assembly characterized in that an inlet and an outlet of two fluids are orthogonal to each other. Assembly. 8. A heat exchanger assembly according to claim 7, wherein the manifold means comprises: a first fluid in communication with the first fluid zone; and a second fluid in communication with the second fluid zone. It features an inlet manifold and an outlet manifold that allow Heat exchanger assembly with characteristics. 9. 8. The heat exchanger assembly of claim 7, comprising a separate first fluid manifold. Make sure that a hold and a second fluid manifold are used for the inlet and outlet. Features a heat exchanger assembly. 10. The heat exchanger assembly of claim 1, wherein at both ends of the core: The second fluid zone is plugged or closed, while the first fluid zone is a first fluid inlet/outlet slot is provided to facilitate passage of the first fluid into and out of the core; A heat exchanger assembly characterized in that it is open. 11. 11. The heat exchanger assembly of claim 10, wherein the second fluid inlet/outlet slot comprises: the sides, top or bottom of said core to facilitate the passage of a second fluid into and out of said core; A heat exchanger assembly comprising: a heat exchanger assembly; 12. 12. The heat exchanger assembly of claim 11, wherein the second fluid inlet/outlet slot comprises: A heat exchanger assembly characterized in that it is provided on the sides near both ends of the core. Li. 13. 6. The heat exchanger assembly of claim 5, wherein each module is adjacent to It is characterized by having a connecting means to enable mutual connection with adjacent modules. heat exchanger assembly. 14. The heat exchanger assembly of claim 1, wherein the surface of the second fluid zone wherein the thermal product is at least 7 times the surface area of each first fluid zone. exchanger assembly.