Method of evaporative cooling to dew point and device for evaporative cooler

FIELD: mechanical engineering; air conditioning and ventilation.

SUBSTANCE: invention relates to heat exchange devices used in air conditioning and ventilating plants, namely, to methods of evaporating cooling to dew point and to plate devices for evaporative cooling. According to invention, plates of plate device are made so that channels and perforation to pass from dry side to wet side can be at least partially wetted with evaporating liquid. Chute is provided made in part of plates which temporarily holds evaporating liquid in contact with wick material on surface of wet side of plate. Evaporating liquid flows along chute through perforation for liquid into following chute. When chute of plate from wet side is from above, perforation for liquid is on side forming reservoir for wetting opposite wick materials. When flow move along dry side, heat is conveyed to plate. In proposed method several heat transfer plates are used. Said plates have wet and dry sides and they form chutes. Plates are wetted form wet sides with evaporating liquid and they pass separately two flows, namely, working and product ones through dry sides. Flow of working gas passes along dry side and gets through perforation into channels on wet side which is cooled owing to evaporation, thermal conductivity of plate and its heat radiation.

EFFECT: provision of more effective air flow and heat transfer owing to evaporative cooling with intermediate coolant.

 

This invention relates to an air conditioning using the evaporating liquid. More specifically, this invention relates to the cooling of heat from fluid (gas, liquid or mixtures with phase transformations or without them) to the dew point for gas by evaporative cooling with an intermediate cooling medium in the heat exchanger, having sent on certain channels the flow of gas and fluid and transverse temperature gradient in the heat exchanger plates. In addition, this invention relates to an improved design of the walls, contributing to the rapid spread of the liquid, an effective system of reservoirs and control system.

Evaporative cooling is an indirect way of cooling the gas stream, usually air, through evaporation of a coolant, usually water, in the presence of the second air flow, and heat transfer from the first air stream in the second. This method has certain inherent advantages compared to conventional air conditioning: reduced energy demand, relatively high reliability and the ability to do without refrigerants such as R-134 (Tetrafluoroethane) and all inconveniences associated with them. However, evaporative Oh adenia an indirect yet is used only in special, special cases of the construction and not on the market as a product associated with place of residence. This is due to certain drawbacks of known devices and methods of evaporative cooling with an intermediate coolant: high cost, inefficient thermodynamic cycle, which does not allow cooling air to a degree sufficient for its intended use, inefficient water supply system, scale formation, bad or expensive heat exchanger, excessive pressure drop, elusive dew point of the air flow (theoretical limit cooling), relatively high dew points in a humid atmosphere, high pressure drop on heat exchangers, bulky heat exchangers and in some designs - having a large number of accessories.

In U.S. patent No. 4.002.040 dated January 11, 1977, owned Mantera and others, describes a heat exchanger in which there is no mixing of air streams directed along certain channels, and in which the flow of air passing through the device performs within device 270 degrees of rotation, causing a large pressure drop caused by the flow path. Furthermore, the design of Munters does not allow for ohlord the deposits of other liquids air, than the outer, and cannot be applied in cases where it is desired recirculation.

In U.S. patent No. 5.187.946 of 23 February 1993, owned Rotenberg, but largely copying the Russian patent Miscenko (2.096.257), describes a heat exchanger having a perforation in the heat exchange plates and alternating wet and dry channels. This invention differs significantly from those described in 5.187.946 (Russian patent Miscenko 2.046.257)where not used: individual processing of food environments (cooled fluid or gas than limited description 5.187.946, or other media), thin plastic plates, which act as effective heat transfer funds from the dry channels to wet, not transferring the heat in the lateral direction along the surface of the wafer, or a small slope of the heat transfer plates to allow efficient wicking action, but instead indicates a relatively large angle. Not disclosed application of the supply of wick or wicks or tanks, instead of using complex and expensive spray heads located in each wet channel. Finally, in 5.187.946 are objections to the use of channel type guide, and approved that turbulent flow provides the best efficiency. However, e is about not allowing the device according to U.S. patent No. 5.187.946 to regulate the transverse profile of the temperature distribution of the individual heat exchanger plates. In addition, in this invention by separating the flow of air from the product, this flow of air is reduced and passes through the perforation channels, reducing pressure drop and at the same time allowing better regulation of outlet channels. The device according to 5.187.946 like device Mantera described above, is limited to the outside air for cooling.

In U.S. patent No. 5.170.633 from December 15, 1992, owned by Kaplan, shows the number of accessories that can grow in the systems evaporative cooling with an indirect. In U.S. patent No. 5.727.394, 5.758.508, 5.860.284, 5.890.372, 6.003.327, 6.018.953, 6.050.100 owned Belding, etc. and Goland and other shows such as the presence of excessive amounts of equipment for air handling. It should be borne in mind that in these systems, such as those mentioned above, one additional heat exchanger increases the overall system cost more than one-third. These systems, however, are used only for air cooling.

In U.S. patent No. 5.453.223 of 26 September 1995, owned by the applicant, describes a device in which alternating sets of wet and dry plates provide two air flow: one dry, cooled by contact with the plates, and one wet cooled using neposredstvennogo evaporation. However, this device requires two gas streams inside and two gas streams outside. In addition, as described in the patent design not only provides cooling an indirect without additional direct evaporative cooling. Although this second stage direct evaporative cooling, which increases the humidity of the treated air is often desirable, it is often undesirable.

Two pending applications of the same inventor also relate to the technology of evaporative cooling with an indirect. In the application PCT/US 01/04082, filed February 7, 2001, describes one way to eliminate the second stage, i.e. the direct evaporative cooling. In the application PCT/US 01/04081, filed February 7, 2001, describes improved methods of design of heat-exchange tubes of the evaporative cooler is an indirect, providing superior hydration and reduced pressure drops.

There is a need for method and device for evaporative cooling of an indirect, providing more efficient airflow and heat transfer. The advantages of an improved bulkhead, tank, and mechanism control device for evaporative cooling premiato the NYM coolant are advantages in comparison with the previously described constructions, allowing you to achieve more positive results.

The present invention is proposed evaporative cooler with an intermediate coolant for flowing media of all kinds, with cross-flow wet and dry channels on opposite sides of the heat transfer plate, which allows the transfer of heat through the plate due to the thin design of plastic or other suitable material, but prevents or minimizes heat transfer in the lateral direction along the plate. For the purposes of this application we want to define some terms:

1. Heat transfer or heat exchange surface has many configurations. They all lie within the scope of the described invention, together with the relevant regulation wetting and flow, as is well known in the industry. We use the configuration of the plate as an example for illustration.

2. Wet side or part of the heat exchange surface means a part having the evaporating liquid on its surface or in it, which ensures the possibility of evaporative cooling of the surface and absorption of latent heat from the surface.

3. The dry side or part of the heat exchanger means of the surface of the heat exchanger, where there is no evaporation in the adjacent gas or liquid. So about the time, there is no transfer of vapor and latent heat adjacent gases. In fact, the surface may be moistened, but not evaporating liquid, or wetted by condensation, but evaporation is not valid.

4. Work flow or the flow of the working gas is a gas flow flowing along the heat exchange surface on the dry side through the dry working channels, passes through holes in the surface on the wet side on the wet working channels, captures steam and using the evaporation takes latent heat with a heat exchange surface, and takes her out on the issue. In some examples, the execution of a work flow can be disposed of as waste, and in other cases it can be used for certain purposes, such as adding moisture or removal of heat.

5. The flow of product or product fluid flow is a flow of fluid (gas, liquid or mixture), which runs along the heat exchange surface on the dry side dry grocery channels and is cooled by absorption of heat by the flow of the working gas on the wet side, absorbing latent heat through evaporation in the wet zone.

6. Grooved wetting system is a characteristic feature of the septum, which in the illustrations is found on all partitions in the Central nervous system, the first partition zone, and gutter adjacent partitions work together as a way of passage of the liquid and as holding cells or tanks for the purpose of wetting the wet side walls. The location and shape and relative placement of these grooved or similar troughs formations here are only illustrations. In the scope of the described invention include other cases of orientation, as well as methods and devices.

Plate in certain places has the bypass channels, or perforation or means for moving the fluid between the dry side of the plate and its wet side, providing for the dry working channels in the wet working channels, which has a direct evaporative cooling. Through perforation is achieved by reduction of differential pressure flow of the working gas in the system.

The method proposed in this invention, allows the separation of the flow of the working gas (which is used for evaporation of the liquid in the wet channels and, thereby, cooling the wet surface of a plate heat exchanger) from the product of the fluid flow, both flow through the dry grocery channels on the same side of the heat transfer plate and both give heat exchanger plate, which on its upper side is cooled by the evaporation of working in the wet channels.

The flow of the working gas first enters the dry working channel, and then through the perforations, pores, or other suitable means of transfer through the plate on the wet side and, therefore, in the wet working channels, where the evaporation of the liquid on the surfaces of the wet channels cools the plate.

On the dry side plates are dry grocery channels. The plate is made of thin material that facilitates heat transfer through the plate and thereby allows heat to pass from the dry grocery channel in the wet working channel. This is one of the main constituent elements of the invention, illustrating the method of separation of flow of the working gas for evaporative cooling of an indirect separated liquid product.

Therefore, the purpose of this invention is to provide a cooling device for evaporative cooling of an indirect, has a perforation that allows the flow of the dry working channels in the wet working channels on the opposite side of the heat exchanger plates.

Another purpose of this invention is to provide a cooling device for evaporative cooling of an indirect, having heat exchanger plates, which do not allow significant transfer of latent heat, h is allow heat transfer through the plate. This allows the temperature transfer through the plate, which is not counterbalanced (average out) the transfer of latent heat in the lower part of the plate. The temperature occurring at the bottom of the plate, should effectively reduce the temperature difference on the plate and rezultirase in low degrees of heat transfer through the plate. Thus, one of the parties of this invention is the presence of smooth heat transfer through the plate from the dry side to the wet while absence of heat transfer along the surface of the plate.

The next objective of this invention is to provide a cooling device for evaporative cooling with an intermediate cooling medium having a temperature gradient across a two dimensional surface of the plate and thereby providing channels of flow of the working gas having a certain temperature range.

Another purpose of this invention is to provide a cooling device for evaporative cooling of an indirect, allowing the choice of product streams of fluid for use in cooling, in particular, can be selected streams of fluid emerging from the coldest grocery channels. On the contrary, you can choose a certain part of the flow of the working gas to provide additional humidity environments is a growing environment.

And another purpose of this invention is to provide a cooling device for evaporative cooling of an indirect, with efficient wicking action that allows you to easily moisten the entire surface area of the wet channels of the exterior of excess water, which cools the water rather than air.

The next objective of this invention is to provide a cooling device for evaporative cooling of an indirect, having a system that ensures uniformity of the liquid in all the wet channels of the device. The system has the property of rapid spread of liquid in all wet walls, providing reservoirs for moisture, and has a control system to regulate and control the distribution of fluid.

Another purpose of this invention is to provide a cooling device for evaporative cooling of an indirect, with the selector cycle, so in the summer months it can be used to provide chilled newlinemode air, and in the winter months to heat from the gases, discharged into the environment with simultaneous humidification space.

And another purpose of this invention is to provide an effective cooling device for COI is sustained fashion with intermediate cooling of the coolant, allowing cooling the product stream to the dew point temperature of the working gas.

And another purpose of this invention is to provide an effective cooling device for evaporative cooling of an indirect, with relatively low pressure drop flow of the working gas.

Brief description of drawings:

Figure 1(a) - spatial perspective schematic view of a first example of the method of the invention, showing the flow path of the working gas to cool the gas during the flow through the perforation or passage from the dry side of the plate to its wet side. On the dry side of the plate has a separating device for providing the path of the working gas separately from the path of product flow of fluid.

Figure 1(b) is a perspective schematic view of the front side of the other plate in figure 1(a), which shows the wet side channels and shows the flow of the working gas, which, after its passage through the perforation flows through the wet surface of the channels, where evaporation occurs.

Figure 1(C) is a perspective schematic view of two plates shown in figure 1(a) and 1(b); on this view shows the wet channels of the hand, formed by the wet sides of the first and second opposite each other of the plates, with their passages, which are located in one and t the th same General region; also shown is the path of the working gas, which is included on the dry side, the current through the passages and into the channels of the wet side. Grocery environment is separated from the working gas as they pass along the dry side of the first and second plates. Dry more adjacent plates should prodigality dry sides of these first and second plates. Thus, in the stack of plates each odd plate oriented dry side in the same direction is opposite to all the even-numbered plates.

Figure 1(d) - spatial perspective schematic view of the second exemplary embodiment of this aspect of the invention, showing the flow path of the working gas, since the separated dry patch included on the wet side through the perforations or passages and extending from one side of the plate after passing through the wet surface wet working channel.

Figure 2 - spatial perspective schematic view of the third exemplary embodiment of this aspect of the invention, showing the path of gas flow in the case where the invention is used for heating and humidifying the air flow.

Figure 3 is a partially spatial perspective schematic view of the flow path of the fourth exemplary embodiment of this aspect of the invention, showing the flow of the working gas in the case when the image is etenia is used for cooling the dehydrated product fluid, and additionally shows the flow of the product fluid in the terms of use.

4 is a partially spatial perspective schematic view of the flow path of the fifth exemplary embodiment of this aspect of the invention, showing the flow of the working gas and grocery in the case when the invention is used with a recirculating gas stream, and additionally shows the gas flow in the terms of use.

Figure 5 - spatial perspective schematic view of the extended block numerous channels, which shows the flow of the dry side, additional perforation and guides additional channels mainly in the middle of the septum. Dry working gas is supplied to and flows through the passages on the wet side (not shown).

6 is a spatial perspective schematic view of the same extended block figure 5, which shows the gas flow wet hand after dry working gas passed through the passages. The surface of the plate is provided with a wicking material for transfer of liquid from the feeder to the edges of the plate and the fluid for evaporative cooling.

7 is a cross section of the block shown in figure 5, with additional plates, showing the gas flow together with side wings, pointing up at an angle from the midpoint. PLA is Tina upstairs has a dry surface. The lower surface of this plate is wet, and the guides of the channels perpendicular to the channels dry side. Wet the surface of the second plate facing the wet surfaces of the first plate, so that the channels between the first and second plates become wet. The second plate has a dry surface at the bottom. Subsequent plates continue to contact surfaces: dry surface to dry, and moist to wet.

Fig is a perspective view of the bilateral core with feed wick plate between two side walls and directed from the center of the upward angle of the wings of the orientation layers of the core.

Fig.9 is a perspective view with a partial tear-out node in this invention, including a schematic diagram of the gas stream and the liquid stream with sloping upwards at an angle wings the core.

Figure 10 is a perspective view with a partial tear-out embodiment of the present invention, in which the insert is used, shown in figure 1(a), and the liquid is fed to the wick material on the plates with the help of the tank. Must be installed subsequent plates with surfaces "dry to dry" and "wet to wet".

11 is a perspective view of a core of two parts with a Central wick stove power between the two wings, and the wings of the slope of the s down from center, and the perforations in each layer is nearest to the Central wick area.

Fig - sample performance of the wick plate power used on Fig, with grooves that run from the highest to lowest point, in order to accelerate the transfer of liquid in the lower part of the wick and allow the drainage of excess fluids.

Fig is another example of execution of the wick plate of food with holes in the inner part of the plate.

Fig third example of the execution of the wick plate power multilayer structure to promote rapid dissemination of fluid around the perimeter of the slab and drainage. The multilayer structure is made of materials with different porosity, and the middle layer has a greater porosity than the outer layers.

Fig is a perspective view of two hearts, similar to that shown in Fig, which shows the path of the air and the separation gap between the two centers to facilitate the transfer of heat through separate paths and, therefore, split long paths that create boundary layers, and those, in turn, hinder the heat transfer.

Fig - site piping and valves tanks together with the plate supply of wicks on Fig, 15 or other examples of execution. The upper reservoir supplies fluid to the plate supply of wicks. By means of a float valve the bottom of the tank is determined by the degree of immersion of the wick in the liquid and with insufficient immersion opens the filling valve, to apply more water in the top tank.

Fig - reservoir system on Fig, combined with the node of the core, shown in Fig.

Fig is a perspective view of another example of the performance of the plate type 1 with wet side at the top, shows the working channels and perforations for gas with a groove made in the plate and having perforations for liquids, so that the latter can pass through the next layer after you reached the specified level in the gutter (in the lower part Fig), and the second grooved plate type 2, such plate type 1, but with a dry top, with food and working channels and perforations for liquids located on the bottom of the gutter (in the upper part Fig).

Fig is a perspective schematic view of the package of plates plate type 1 and plate type 2, and the second plate of the type 1 and the second plate of the type 2 and the third plate type 1 and the third plate type 2; shows the path of the fluid when it enters the upper part of the chute plate type 2 of the plate above it and out through the perforations for liquids getting into the groove of the next lower plate, plate type 1, where the liquid accumulates in the reservoir until then, until you reach the level of the perforations for fluid on the sides of the trench, and then she goes and falls in the groove of the next lower plate type 2, and so on. LM the bone, thus, the falls cascade down from the tank into the groove of each plate type 1.

Fig is a perspective schematic view of the plate pack type 1 and type 2 with a tube of liquid supply for supplying liquid to the upper trough this package has a top plate and a shutter working air regulation air and liquid passage.

Fig is a perspective schematic view of the plate pack type 1 and type 2-like package on Fig with the tubes of the fluid at more than one level, and the bottom reservoir for collecting fluid from the control device to determine the need to add liquid in the package.

Figure 1(a) represents a spatial perspective schematic illustration of an example of execution of the main element of this invention, showing the manner of cooling an indirect. The element is in the form of a flat plate (referred to here as plate 6)having perforations 11, which connects the dry side 9 with wet side 10. Dry fitting 9 is divided into grocery channels 3 and a dry channel 4 to the working gas; perforation 11 in the channel 4 of the working gas. Wet side 10 (see figure 1(b)) for cooling moistened evaporating liquid. Wet side 10 also has a wet channel 5. Dry channels 3i 4 (figure 1(a)) are separated so that dry working gas is kept separate from the dry grocery fluid. Guides 8 channels limit dry channels 3 and 4 in such a way as to prevent mutual mixing of gases from these channels and at the same time to provide a relatively free movement of gases across the plate 6. Since the plate 6 is very thin, the heat can easily pass through the plate perpendicular to it with the dry side to the wet side. The plate material is selected in such a way as to minimize heat transfer along the plate. The preferred material is plastic. The materials of the guide channels in addition to providing the boundaries of the channels can also isolate flows, to the extent possible, from the adjacent parallel threads on both sides, thereby providing a low degree of parallel heat transfer".

When the device product stream 1 the fluid and the flow 2 of the working gas are introduced respectively into the dry channels 3 and 4, crossing the dry side of the plate 6 in the laminar regime. Thread 2 working gas then flows through the perforations 11 on the wet side 10 in the channels 5. Wet wet channel 5 parties direct the gas stream 2 to some extent, perpendicular to perpendicular to the fluid media flowing through the dry side and across the wet side 10 of the plate 6, the DG is he gets heat in several ways: first, due to the evaporation of liquid from the wet side 10 and, secondly, as the heat given conduction and radiation plate 6. Thus, the plate 6 works as a heat exchanger and as evaporative cooler with an indirect. Thread 2 gas exits the evaporative cooler 6 with intermediate cooling medium to flow 2 gas, as shown in figure 1(a) and Fig.1(b).

Cross the stream need not be exactly perpendicular, while it is to some extent perpendicular". When rotated 180 degrees, the thread becomes the opposite stream, and at 0 degrees streams on both sides of the plate 6 may be parallel. To some extent perpendicular to the flow can occur when the angle between these extremes, provided that this angle allows threads on opposite sides of the plate cross each other. The importance of flows on opposite sides of the plate 6 is that it provides a temperature gradient and the temperature difference described below.

In this embodiment, all of the threads 2 working gases pass through the center of the plate 6 on the dry channel 4. On the face of the plate 6 under a dry channel 4 flow 2 gas comes into contact with the wet side and is cooled by evaporation. At the entrance is Otok 2 (on the dry side in the channel 4) is cooled by evaporation on the front side of the plate 6. This process is pre-cooled stream 2. Thus, when the flow is directed down the channel 4 on the dry side before entering the perforation 11, he dry cooled to the perfect temperature to wet bulb temperature. This pre-cooling on the dry side allows a thread to enter on the wet side, having a temperature lower than the initial temperature.

The direction of the gas streams 1 and 2, in addition, improves the efficiency of the device due to the possibility of regulating the flow and temperature of the stream. The temperature difference across the plate 6 is created by passing the gas stream 2 through the wet channel 5; at the beginning of the flow of the gas stream 2 wet channel 5 it is very dry and can absorb the maximum amount of steam evaporated from the fluid. This, in turn, absorbed the maximum amount of latent heat (conversion of liquid to vapor), which allows a greater temperature difference on the wafer 6. Therefore, the channel 3 that is closest to the channel 4, will be cooled to the maximum extent possible.

In practice, grocery fluid medium can be any medium (air, gas, liquid or mixture), for which it is desirable to dry cooling, i.e. cooling without adding gas component under partial pressure, obtained by evaporation of the coolant is hidcote. For example, if an industrial or associated with the place of residence using a fluid medium may be air, and the coolant - water: the product streams of air coming out of the TV with a dry hand, in this invention do not increase the humidity. You can use refrigerants or during phase transformations or not to allow cooling to low temperatures before use and thus to achieve a higher efficiency of the refrigeration cycle at a low cost.

In the example implementation shown in figure 1(a), dry branch working gas 2 from the product fluid can be performed with the help of the guides 8 channels, which act as walls between adjacent plates. The fence or wall 12 at the end of the dry channel 4 prevents the yield of dry gas and mixing it with a grocery fluid medium. If the plate 6 has folds or corrugations, guide channels partially provided by these folds. The guides should be placed on each, that is, on both sides of the plate 6 and between the food environment and working gas to prevent the passage of fluid between the folds of the opposite plate. In each case, they function as the direction of the gas or fluid in a certain direction, and in those cases, the implementation of the population, where there is more than one heat transfer plate, can also contribute to the separation plate 6 from the other plates. In addition, in cases when there is no need for additional separation, fold guides can be used between the flat plates 6.

Wet side 10 of the plate 6 may have a layer of wick material, can cause the coolant to wet side 10. Preferably, the wicking layer may cover the entire surface of the wet side 10. For wick layer, you can use any of a large number of well known materials such as cellulose, organic fibers, fibers based on organic, porous plastics, fibers are carbon based, polyesters, polypropylene, fiberglass, fiber-based silicon and combinations of these substances. A layer of wick material can take various forms: films, fabrics, cords, layers of particles, e.g. beads, and combinations thereof.

Preferably, the wick material layer may be a material of the plate 6. For example, the plate 6 may consist of a wick material treated with one hand so as to make it waterproof and waterproof side is used as a dry side of the plate 6. Treatment may consist in changing the nature of the wick material or the freight of his other stuff, for example, a plastic film or the like. Wick material can be processed to obtain low permeability instead of the full water resistance. In this application "low permeability" means that the amount of water flow through the plate 6 on the dry side 9 is sufficiently small so that the gas flows crossing the dry side 9, not moisturizing and not cooled by evaporation. Replacing the dry side with low permeability on the dry side with a full waterproof, yet allows for the practical use of this invention as here claimed.

On the contrary, the material of the plate 6 can be waterproof and processed to turn it into a porous or wick on the wet side 10. In any case, the material of the plate 6 must have a relatively high resistance to heat transfer. While it is almost not influenced by the heat transfer across the plate because of its small thickness, the heat may not be transferred in the lateral direction along the plate, as indicated earlier.

The plate 6 may also receive the coolant from the supply wick, as will be described below with reference to other embodiments.

The perforations 11 may be round or have other shapes without corners, or such forms, ka is a rectangle with rounded corners, not only to increase the durability of the plate, but also to help prevent turbulent flow 2 gas when it passes through the perforation. By preventing turbulence pressure difference across the evaporative cooler with an intermediate cooling medium can be minimized while increasing the efficiency and reducing the cost of construction. Perforation may comprise passages, such as micropores, rather than the perforation.

It is desirable that the plate 6 had the inclination, to prevent the accumulation of excess water and/or to allow the bottom edge of the plate 6 to be in contact with a source of coolant, such as water, whereby a wick material could implement a continuous supply of cooling liquid on the wet side 10. In the presence of a very small tilt of approximately -10 to +10 degrees, the flow of liquid on the wet side 10 is much more effective. At large angles the maximum possible height of the wick material unduly restricts the width of the plates. In extreme cases, the flow may be ineffective or impossible, thereby reducing the amount of evaporative cooling due to inadequate quantity of cooling fluid deiparine. Depending on the nature of the wick material, the wick may not apply the liquid on the entire surface of the wet side 10, leaving some areas of dry, or leave some areas without a quantity of liquid sufficient for effective evaporation, creating a high level of relative humidity in the flow of the working gas. Thus, small angle ensures much more efficient wicking action and given the maximum height of the wick allows greater width.

The plate 6 may also have a V-shaped cross-section with double inclination, as shown in Fig.7 and 8, that is, the plate 6 may be similar in cross section to a small saddle, the middle part is lower than the two opposite edges or wings. Two sloping parts can have different lengths or different angles or may vary with the nature of the wick material or other factors.

The plate 6 may also be equipped with the "cutter select stream (not shown)to allow the selection of only the most cold gas streams on the dry side of the plate 6 (can also be incorporated into the design of the web clipper to select the working gas specific humidity to increase the humidity of the environment in the Central part of the plate), or all of the gas streams, or some intermediate choice. By p the vacation only the most cold streams for use in the cooling provided less but cooler gas flow; the use of a wider range of gas flow provides a greater flow of gas. The cutter may also choose wet working gas for use in moist environment.

Figure 1(d) represents a spatial perspective schematic view of a second embodiment of the element of the present invention. In this embodiment, the plate 6 has perforations 11, which is located along one of the sides, not in the middle, as in the previous embodiment. Guides 8 channels form a dry channel 3 and channel 4. In this example, the guides 8 are the edges, but can be and guide other types, as mentioned above. The guide 8 is also used to prevent the flow of gases over one of the edges of the plate 6. Thread 2 working gas flows through the channel 4, the product stream 1 flows through the channel 3. The gas flow 2, that is, the working gas flows through the perforations 11 in the channel 5 (not visible), and then flows across the front side of the plate 6, leaving the plate 6 in the form of a gas stream 2.

Figure 2 represents a spatial perspective schematic view of a third embodiment of the invention, showing the path of gas flow, when the invention is used for heating and humidifying the air stream with water. Therefore, in this example, the flow of gas could is t be considered as air flows, and under the cooling fluid may be water. In the winter months, the best heat transfer between the air leaving the heated space, and cold fresh air coming from the atmosphere, that is, outside air, or air from another source in the environment. This reduces the amount of heat required to heat the fresh air. This invention also allows the addition of moisture in the fresh air, thereby turning to another winter problem: cold outside air, which contains condensed moisture and, therefore, has a low absolute humidity, or extremely dry air, which is accompanied in the dry interior air when the humidity inside is reduced due to air exchange with outside fresh air. "Select cycle", i.e. the air flow that goes into the atmosphere, and the flow that enters the conditioned space, is a characteristic feature of embodiments having such a device.

In figure 2, the plate 6 has a dry side 9, the wet side 10, the guides 8 channels and perforations 11. Thread 1 air comes out of air-conditioned space. At the same time fresh air 2 enters and flows through the perforations 11. As shown in the previous two embodiments, the plate 6 acts as a heat exchanger, thanks diploproa the particular removing heat from the stream 1 air on the dry side 9. Thread 2 air flows through the wet side (not shown) and other parallel channels for receiving heat in two ways (via conduction and radiation) and humidity (due to evaporation) from the wet side 10. Wet side 10 may have a wick material, as described above, and the design of the plate 6 about permeability, materials, processing, supply of wicks, guide channels, folding, perforating, cut off selection cycles, etc. may also be such that what is described above. In this way, the energy that is already used in a warm air stream is stored, and the flow 2 of fresh air is added moisture.

"Cutter selection cycles (not shown) provides the capability of switching between a cooling cycle and a heating cycle-wetting. The easiest way to cut selection cycles can be used to select a thread that should be in conditioned space or air, which passes only on the dry side 9, or air, which runs on the dry side 9, and on the wet side 10. The cutter can also provide different sources for streams 1 and 2 of the air, as should be clear to all specialists in this field.

Figure 3 is a partially spatial perspective schematic view of a flow path for the version Khujand is the implementation of the invention, showing the gas flow in the case where the invention is used for cooling, and, in addition, shows the gas flow in the application. In this embodiment, one of the threads of the gas is air from the conditioned space. Since this air is extracted from the conditioned space, it is often colder and drier than the outside air, or colder than dry air, it can be used as a working flow in the evaporative cooler according to this invention.

Plate 6 evaporative cooler with an intermediate coolant contains guides channels and perforations (denoted collectively for convenience as 11). Dry grocery flow 1 the air is dryer 25 and enters the channels 3 on the dry side. Leaking on the dry side of the plate 6, it gives off heat in the plate 6, leaving the cooler, but without additional moisture. The air exits from the conditioned space 24 in the form of a stream 2 of the working air that flows through the channel 4 plate 6 evaporative cooler is an indirect, where he before pass through the perforation 11 in the channel wet hand, gives some heat to the plate 6 by heat conduction. On the wet side of the plate 6 thread 2 air is cooled by evaporation and at the same time Oh what Agdal plate 6 by the same action.

The desiccant 25 may contain liquid or solid desiccant known type. The desiccant 25 must be re-charged, that is, to provide the ability to remove the water absorbed from the stream 1 of air. This is done by regenerating air 27, which before entering the desiccant 25 is passed through the heater 26. The moisture absorbed from the stream 1 of the air is removed from the desiccant by the high temperature regenerative air 27. To transfer heat from the flow 1 air after this thread will be heated and dried by passing it through a desiccant 25, regenerating the 27 air before it is heated in the heater 26 you can use the optional heat exchanger; this method is known in the art. However, you should appreciate the fact that neither in this example implementation, nor in the preferred examples described below, such additional heat exchanger is not used, since this invention provides highly efficient cooling to the dew point, and the additional heat exchanger increases to 45 percent of the cost of the entire system.

Figure 4 is a partially spatial perspective schematic illustration of the flow path of the fifth embodiment of the present invention, showing the gas flow, when the invention is used with cirkuliruyusiy flow of gas, and, in addition, shows the gas flow in the application. In this example of the invention, air from the conditioned space is again cooled and returned in the form of product fluid. This results in energy savings and additional cooling of the product stream of air.

The plate 6 has guide channels, the channels and perforations 11. Thread 1 air leaves the dehumidifier 25 before passing through the channels of the dry side of the plate 6, where it gives up heat to the plate 6 by heat conduction. The air stream 1 is then held in air-conditioned space 24 and, ultimately, recycle in the drier 25.

Directing channels separate thread 2 working air from the product flow 1 air after a dryer 25. He passes through the channel, which gives off heat to the plate 6 and flows through the perforations 11 on the wet side of the plate. As in the previous embodiments, the wet channel is not visible, but the arrows that show the flow of the working air, show that on the wet side, there can be multiple channels. At the same time thread 2 working air absorbs heat from the plate 6 by evaporation, radiation or conduction, the cooling plate 6.

5 and 6 are spatial perspective schematic images of a large plate containing the elements of this image is the shadow; shows the gas flow on the dry side, the gas flow on the wet side channels, which are not shown, but is represented on the obverse, an additional perforation and guides additional channels, and Fig.7 is a cross-section of figure 5 and shows the gas flow on the wet side.

Evaporative cooler has a product gas flows, the flow of the working gas, grocery channels operating channels, canals, wet hand, wick material, guide channels, the dry side wet side, perforation, block and openings of the supply fuses.

In operation, the flow of the working gas or grocery fluid flow respectively through the dry channels 4 and 3, transferring heat in the heat exchanger without increasing humidity. The flow of the working gas flows through the perforations in the channels 5 wet hand. 7 and 8 shows that the evaporative cooler contains many plates (three diagrams respectively showing one 5, two and three plates 7, but the number of plates is not limited to, Fig). Plates can be "identical" in the sense of available channels on both sides of the associated perforation 11, allowing the gas flow to flow through plate made from materials having a low degree of heat transfer in the lateral direction, and impenetrable on the one hand, with dry sides opposite one the other through the gap between the plates, and other wet sides. The plates are arranged in parallel and have similar side, facing each other. In this application the expression "similar sides, facing each other" refers to the fact that the wet side facing the wet sides of the other plate, and dry side facing the other plate. This does not apply to the location of the perforations 11, which will be described below.

In the channels of the wet side of the air stream receives heat from the plates evaporative cooler; heat transfer mechanism described above. As indicated earlier, the thread 2 of the working gas is pre-cooled through its passage through the channel 4 dry side plates, what is the additional cooling effect of the device proposed in this invention. In addition, as mentioned previously, the flow of gas can be selected on the basis of the variation of heat (cooling) for use as either the product or the working air, or humidity, or without it. Thus, the plate 12 (see Fig) locks the ends of the channels 4, requiring that the entire flow 2 air passed through the perforation 11 in the channels of the wet side. Under different conditions, some part of the thread 2 of the air can be allowed to pass through the end of the channel 4 by removing the plate 12, resulting in a greater volume not is how many less cold food air or otherwise, some part of the flow 1 air may be rejected or locked (that part of the thread 1 of the air, which was the farthest from the center of the evaporative cooler 6 and therefore suffered the least cooling), resulting is fewer a little more cold food air. Other alternative designs proposed in this invention are the same as described previously.

Thus, air flows in this block flow between two plates, and not through one plate. If two such plates have dried by the parties to each other, the streams of air will flow between the two plates on dry sides, as if to draw together the wet side, the streams of air will flow between the plates wet sides. In embodiments having more than two plates, the air will first flow between the dry sides of the two plates will then flow through one or both of the plate and to enter into the wet channels through which they will flow through one or two of the same plate (on the back) and the wet side of the third plate.

In one embodiment, wick through the hole 23 may be feeding wicks 13 for supplying water to wick material 7 that will be described in connection with Fig and 9.

Fig.9 is a perspective view h is a partial dug another example embodiment of the invention and includes a schematic diagram of the gas flow, which can be seen under two different angles.

Evaporative cooler 14 with an intermediate cooling medium has an approximately box-like shape, although the shape can be optimized by adapting to the specific conditions that are well known in the art. Many of the plates 6 forming the package. Each of the plates 6 has a wet side 10 and a dry side 9, although for clarity, reference is made only on the top plate 6. Plate 6 are arranged in parallel and facing each other such parties, so that the wet side 10 facing to wet the sides 10 and the dry side 9 facing the other dry sides 9.

Preferably, these plates 6, in which the perforations in the adjacent plates is not located on the same line. Instead, in preferred embodiments of this invention, the perforation 11 is offset relative to the perforations 11 in the following plate 6. This helps to reduce the pressure drop across the evaporative cooler 14, which reduces power consumption and increases efficiency. In addition, you have better air distribution in the wet evaporative channel 5.

The cooler 14 also has a reservoir 17 for the water pump 15 and the supply fuses 13. Water 7 is drawn out of the tank 17 by the pump 15 and is served up to a power supply fuses 13. Line 8 re-fill the tank allows you to continuously replenish the water in the tank or refill it if necessary.

Although the gap between the plates (dry and wet channels) for some gases or liquids can be of any size, the gap between the plates 6 plays an important role in the effective application of this invention. If the gap is chosen properly, the pressure drop of the gas streams passing through the proposed device is significantly reduced, providing either a greater flow or the ability to use smaller fans. The experiment showed that it is preferable interplanar gap of 1.5-3.5 mm, and most preferred are gaps in the range of 1.50-1,85 mm, 2.00-2.35 mm, 2,10-2,90 mm and 3,10-3,50 mm When these gaps occur standing waves, reducing the resistance in the process flow. It is also possible that if these gaps are not supported turbulent (reliminary) stream, which may also serve to reduce the resistance and pressure drop in this particular process. A proper gap can be maintained separate structural elements (not shown) or preferably may be provided with guide channels 8 of the plate 6, which may be provided with ribs or other means.

Supply fuses 13 are tubes that carry wicking material covering at least part of the outer surface of the tube. The holes in the tubes allow the water 7, inside the tube, to achieve and to moisten the outer wick material which is in contact with the wick material 7 on the wet side 10. Water 7 flows out of the holes on the outer wick material. Then the water can flow from the wick material feeder to wick material 7 wet sides 10 and spread to those parts of the wet sides 10, which is covered with a wick material 7.

The product stream 1 fluid enters the dry channel 3 and the thread 2 of the working air enters the dry channel 4; both are on the dry side 10 of the plate 6. The flow of the working air passes through the perforations 11 in the channels 5 moist hand, the cooling plate 6, as described above. Note that for clarity, only four of flow of air can be seen coming out of the cooler 14 and only one member; in fact, there may be any number and they can go (and in this preferred embodiment, and face) from both sides of the cooler 14.

Directing channels serve several functions. In addition to the separation of flows 1 and 2 air they subdivide these streams advanced, thereby improving the temperature distribution in the proposed device, creating channels that bring cooler grocery 1 air near the center of the plate 6, help to generate flow with one hundred is CIMI waves or laminar flow, thereby reducing the pressure differential on the device, and help to isolate the parallel division of air streams 1 and 2, thus preventing parallel heat transfer. Finally, guide channels also serve as structural elements for supporting the package and the separation of the plates 6 desired distances.

Plate 12 (shown in Fig and 9) prevents the output of the working air 2 from the device through the dry channels 4, thereby enhancing flow in the wet channel 5. In other words, the output of the wet channel 5 will always be lower stream than the perforation. As mentioned above, alternative embodiments in accordance with the specific requirements and conditions of a certain part of the product air may also be delayed or rejected, and some portion of the working air can be produced as a product of air.

As mentioned above, the degree of pre-cooling, which is exposed to the flow 2 of the working air, is partly determined by the choice of the dimensions of the perforations and channels. As mentioned above, the material of the plate 6 provides negligible heat transfer in the lateral direction, which, in turn, creates a temperature difference or gradient in the lateral direction on the plate 6. The selectors select cycles (not shown) mainly m which may be applied to select, what unit of streams 1 and/or 2 air used for air conditioning, thereby allowing a greater degree of cooling than otherwise, and also to provide flexible control of temperature, humidity and amount of product gas.

Under the numerals 19 and 20 (see Fig.9) schematically shows the fan blower or equivalent device, but the subject of this invention provides an alternative performance of the ventilation device. For example, to ensure both production and product streams 1 and 2 air as a means of forced draught can be used one fan. In addition, the intake fan has advantages over the exhaust. Due to the evaporative process used in the device, the parasitic heat added by the fan motor to the air streams 1 and 2, is effectively used for incremental evaporation of water 7 and thus helps in removing himself resultswas in a small Addendum to the final temperature of the product stream 1 air. Intake fan provides the air and into the working channel of the air, and in the channel grocery air in accordance with the pressure drop in each and every from the exterior of selectors that can be used. Finally, because the worker and the product air is routed through different outputs, requires two fan for drawing two threads, but only one for injection of both threads.

Package 14 (see Fig and 21) may be enclosed in a casing (not shown), which may further guide and regulate the air flow and to improve the aesthetic quality of the device. The casing can have inputs and outputs for flow of product and working air and cutter selection cycles. For example, when the cutter is set in the first position, it can cause the chiller to operate in normal mode, and when the cutter is set at the second position, it can get heated moist process air to become the product air. Together with recirculating air this phenomenon can be used, as described above, to provide hydration and pre-heating of the winter air.

As in the previous embodiments, the evaporative cooler 14 with intermediate cooling agent can be used together with the flow of recirculating air drying devices, folded plates and apply material handling plates, perforations and other details.

It should be noted that the evaporative cooler is an indirect, proposed in the present invention, may be performed as a direct evaporative cooling, so isparitelnoe cooling an indirect product flow 1 air. Part of the dry sides 9 can be moisturized by applying wick materials used to wet the sides 10, or otherwise to cause further cooling of the product stream of air. This wet part dry the parties may preferably be located downstream from the driest part of the dry sides, so even before the moisture in the process of direct evaporative cooling appreciable temperature of the product stream 1 air decreases as possible. One of the special advantages of this situation is that approximately below 65 degrees Fahrenheit moderate increase in humidity causes a disproportionate decrease in temperature in accordance with conventional psychrometric tables. In another embodiment of the present invention, this irrigated part of the dry side of the plate is 25 percent of the surface area of the dry channel 3.

Figure 10 represents a spatial perspective schematic view of another embodiment of the present invention, showing the gas flow and the water tank.

Evaporative cooler 6 has a dry side 9, the wet side 10, a grocery flow 1 air and stream 2 working air guides 8 channels, dry channels 3 and 4 and the wet channel 5, and the tank 17 on the water. In this embodiment there is no need for a water pump for a wick system, because the wick material wet sides 10 is located directly in the tank 17 to the water. However, the width of the fins of the cooler 6 is limited by maximum height of the wick material, if the plate is not inclined, as described earlier, and the tilt also allows a more efficient wicking action. This alternative implementation is also an example of the evaporative cooler is an indirect according to this invention, which uses the issue from only one side of the plates.

On Fig two wings of the core extended outward and upward from the center. In the center, as shown, is the plate supply wick system, which informs the liquid used for evaporative cooling in the wet channels, with layers wick material core.

On Fig wings extended upward at an angle between approximately 0 degrees and +10 degrees. An alternative option is shown in figure 11, where the wings extended from the center down within the approximate range of tilt from 0 degrees to -10 degrees.

The choice of the inclination of the wings up or down will also include the choice of wick material on wet surfaces, so that the liquid can move across poverhnostnogo material on each plate.

The advantage of the slope down is that the liquid can more easily reach the edges due to the additive action of gravity. This will help reduce the formation of scale on the edges which may occur when using fluids with mineral admixtures.

Added help of gravity (or tilt wing down) is that you can wet the wings of greater length from the Central wick feeder and this process will be faster.

The result of the accumulation of excessive amounts of water on the outer edges of the wings when they tilt down will be the formation of liquid droplets. Also when cooling the excess water excess cooling fluid only lowers the efficiency of the evaporative cooler. To minimize the accumulation of excess water, wick material layers must be less porous than the supply wick.

Wings raised at an angle upward (Fig), will not carry extra water from collecting on the edges of the layers. A more likely result will be lack of water reaching the outer edges, which will cause the deterioration of the cooling and accumulation of minerals on the dry edges.

Examples of execution of the plates 13 wicking power, shown in Fig, 13 and 14 show the improved design of solid slab wick power. The purpose of the imp is in grooves 50 (Fig), holes 51 (Fig) or multilayer structures (Fig) is creating the possibility of more rapid movement of the fluid from the upper part, where the fluid is introduced into the stove wick power, in the lower part and, thus, faster moisture wicking material core. Alternative methods include installing rods 57 located along the lateral sides of the supply fuse (see Fig).

Channels, holes and more porous core of these embodiments of the invention will allow the liquid to move across the plate supply of wicks and, thus, to promote the evaporation of the liquid.

Channels, holes or core may not extend all the way to the bottom of the power plate wicks, in order in this way to allow the liquid is very easy to pass along these routes before humidification of the feed wick.

On Fig shows the set of sections of the core with a gap 55 between adjacent sections. This gap functions as the separation of the air flow directed on certain channels into separate parts. This, in turn, reduces boundary layers in the channels, preventing efficient heat transfer. At low speed in the channels of the fluid medium tends to laminar flow. In the boundary layer closest to the plate, in the dry channels of the degree of heat transfer t is aetsa low. This boundary layer is negligible at the entrance plate and grows along stream forward, so the degree of heat transfer is much higher at the entrance of the channel and decreases exponentially to some smaller constant value.

On Fig and 17 show examples of the performance of the system reservoirs together with the core and the plates of food wicks.

The upper reservoir 60 delivers the liquid to the plate supply of wicks. The upper tank is equipped with a valve and a tube with the appropriate fluid. When the liquid from the tank is fed in the feeding wick, excess fluid flows into the lower tank 61.

Float valve that is sensitive to the liquid level in the lower tank actuates filling valve 63 of the upper reservoir.

When the wick picks up the liquid in the wick material on the layer of the core, the upper reservoir 60 is emptied. If evaporation exceeds the flow of the liquid in the lower tank 61, the float 62 will be omitted. He drives the filling valve 63, adding water to the upper reservoir 60.

When the plate 13 power wicks served more fluid than can evaporate, the residue is collected in the lower tank 61. When the float rises and closes the filling valve upper reservoir. This system requires constant release of water from nignog the tank, so it is sensitive to the intake of water into the system. This constant release also helps to prevent the concentration of minerals.

Thus, the evaporation rate determines the need to add or reduce the amount of liquid in the supply wick.

Additional characteristics of this variant implementation is the overflow shutter 64 and the system 65-off and drain. In any well-known systems, the flow of the liquid in the reservoir can be regulated by thermostat.

On Fig shows another example of performance of the heat exchange plates, namely plate 70 type 1 with groove 72 in the lower part and the plate 71 type 2. Perforation 11 plates of type 1 and 2 flow 2 gas is out of the gutter. The groove 72 is used to hold and distribute the liquid 1 used to wet the sides of the plate. In the plate 70 type 1 visible wet side 10 with wick material 7 on the surface and the visible surface of the trench.

The perforations 73 in the chute is intended for the passage of fluid to the next layer. When the wick material 7 on the upper part of the wet side perforation 73 is located on the lateral sides of the chute 72. This allows fluid 74 to remain on this layer to wet the wicks out of the sides of the plate. Perforation 73 on the sides of the chute allows the filling to this level. This chute 72 h the next layer above (or plate 71 type 2) with a wick layer on the bottom side will be partially immersed in the liquid in the tank 74 and thus the wick material of this layer will be fed moisturizing fluid this tank 74. Both opposite the wet surface will receive the liquid from one tank.

On the wet side channels 5 of the working gas are arranged at an angle to the outer edges, as in other examples of implementation, and receive a working gas with 2 dry side 9 through the perforations 11, as in the other examples. The flow of the working gas 2 helps spread the liquid out on the wet side of the plate.

The plates 71 type 2 grocery channels 3 and work the dry channel 4 are separated guides 8 channels. Perforation 73 for fluid is located on the bottom of the gutter, allowing liquid from the reservoir plate, located above, or from the supply tube 75, to flow down into the reservoir of the next plate below.

If you have many plates with opposite damp parties forming working wet channel 5, and right sides, forming a dry channels 3, gutters are inserted into each other. The liquid 1, where it was not included in the package, will fall down the cascade, going in every gutter type 1. This flow is shown in Fig.

On Fig shows a more complete package 14 with the supply tube 75 to distribute the liquid in the upper chute. At the ends, as shown and Fig, there is a boom 12 for sealing the dry channel 4 working gas to be sent after the deposits through the perforation 11 in the adjacent wet working channels 5. Grocery channels 3, as Fig, are separated from the channels 4 of the working gas for the dry side of the plate.

Fig such pig and depicts the package 14, which uses the groove 72 with two feeding tubes 75, one on top and the other at the secondary level. This allows the fill tank 74 for rapid actuation. This can be done and in other ways known in the art, for example, using the set of input points. The sensors 76 show the liquid level in the lower tank 61. If the level is too low, the controller opens the filling valve 63 to submit more fluid in the tube 75. On the contrary, if the lower tank is too full, the flow in the supply pipe is interrupted. The use of liquid wet channels for evaporation reduces the fluid flow, which minimizes the amount of fluid received by the lower tank 61. When this situation occurs, the sensor 76 detects the low level and sends a signal to increase the fluid. The sensors 76 may be located in the wet channels, or in the package 14, or in the gutter, it is clear that all professionals in this field.

The use of plastics, cellulose or other flexible materials unacceptable for partitions of heat transfer in some applications associated with the condensation of refrigerant or steam. In these cases, as well as for others, Estrich, having wall structures, such as tubes, with the walls having a heat transfer surface, it is necessary to apply a metal, such as aluminum.

Thanks preliminary condensation of refrigerants and other activities mentioned here in the process of evaporative cooling with intermediate cooling agent in this invention is required less pressure gaseous refrigerant, and the saving of heat and electricity.

Use these hearts more profitable than cooling towers or similar devices that can fit in the system associated with the housing.

The invention and examples of its implementation, described herein, allow many equivalents, alternatives and additions without deviation from the scope of the invention. This description is not a limitation of the volume, which is defined by the attached claims.

1. Evaporative cooler (14) an indirect containing

a) several plates (6)with dry (9) and wet (10) side, and the wet side is designed in such a way that at least partially wetted evaporating liquid, plates optionally form at least one first channel (4) on the plate for flow direction (2) of the working gas through the dry side of the plate, the second spacecraft is Aly (3) for the direction of product flow (1) of the fluid through the dry side of the plate and third channels (5) for directing flow of the working gas through the wet side plates;

b) trough (72)formed in the plates, to hold and transfer the evaporating liquid on the wet side plates;

c) in which the plates are arranged parallel to each other with clearances and are oriented so that their wet sides were facing each other and their dry sides are facing each other, and in which during operation the flow of the working gas from the dry sides of the plate flows into the gap separating plate to wet the sides; and in which during operation of the product fluid passes through the dry side of the plate and cooled to them.

2. Evaporative cooler with an indirect under item 1, in which the gap between the plates is selected such as to minimize the pressure drop of the gases flowing between the plates.

3. Evaporative cooler with an intermediate cooling medium, under item 2, in which the size of the gap between the plates is from 1.5 to 3.5 mm

4. Evaporative cooler with an intermediate cooling medium, under item 3, in which the size of the gap between the plates is in any of the following ranges group: 1.50 to 1.85 mm, from 2.00 to 2.35 mm, from 2.10 to 2,90 mm, 3,10 to 3.50 mm

5. Evaporative cooler with an indirect under item 1, additionally containing perforations (11) through the plate, configured in such a way that the s to allow the worker to flow through the perforations from dry plate to wet the plate and continue to flow through the wet plate.

6. Evaporative cooler with an intermediate cooling medium, under item 5, additionally containing a boom (12)having such size and configuration to prevent the output of the working flow of the evaporative cooler before this thread will pass through the perforation.

7. Evaporative cooler with an indirect under item 1, in which one or more channels on the dry side (4) is oriented at an angle to one or more channels (5) on the wet side, so that the direction of flow of fluid through the dry side of the plate, essentially perpendicular to the direction of flow of gases through the wet side of the plate.

8. Evaporative cooler with an indirect under item 1, further comprising an element for draining product flow and workflow before passing them through the dry side of the plate.

9. Evaporative cooler with an indirect under item 1, further comprising a humidifier (25) and means for passing at least one of the threads - product flow or work flow - through humidifier before passing this stream through the plate.

10. Evaporative cooler with an indirect under item 1, in which the product stream is recycled from the space to be cooled to be reused as a workflow and/or product stream.

11. Evaporative cooler with an indirect under item 1, in which the channels form guides (8) channels containing either multiple edges, extended parallel to the direction of flow of fluid through the said side plates and the mating surface of the adjacent plates, or fold plates.

12. Evaporative cooler with an indirect under item 1, used either for cooling any space, or to facilitate the heating and moistening of this space, and additionally containing a cutter selection cycle having a first and second position, so that when the cutter selection cycle is in the first position, the flow of the working gas is vented to the atmosphere, and the product stream is directed for cooling the said space, and when the cutter selection cycle is in the second position, the product stream is vented to the atmosphere, and the worker thread goes for heating and humidifying the mentioned space.

13. Evaporative cooler with an indirect under item 1, additionally containing at least one fan (20)located in such a manner as to cause the movement of the product of the fluid flow and the flow of the working gas.

14. Evaporative cooler with an indirect under item 1, in which the gutter is perforation (73) for liquids, have intervals in such a way as to allow fluid to leak out of the gap between one set of wet sides in the gap between the other set of wet sides.

15. Evaporative cooler with an indirect under item 14, in which the perforation fluid in alternate troughs shifted so that fluid flows around the gaps between the dry side.

16. Evaporative cooler with an indirect under item 14, additionally containing on the wet side plates wick layer for distribution of liquid to wet the sides.

17. Evaporative cooler with an indirect under item 1, additionally containing on the wet side plates wick layer for distribution of liquid to wet the sides.

18. The method of evaporative cooling to the dew point, characterized in that

a) apply several heat transfer plates (6), and the plates have a wet side (10) and the dry side (11) and form a trough (72);

b) have a plate in parallel so that the wet side of the plate facing the wet and dry side facing toward the dry side of the wafer;

c) place the evaporating liquid in the trough;

d) moisten the wet side of the heat transfer plates evaporating liquid;

e) proposalrace thread (2) the fluid through one part of the dry sides of the heat transfer plates;

f) let the product flow (1) of the fluid through another part of the dry sides of the heat transfer plates;

(g) pass the working thread through the wet side of the heat transfer plates;

h) is cooled heat transfer plate by evaporation evaporating the liquid working stream to wet the sides of the heat transfer plates;

i) is cooled product stream and a work flow by contact with the cooled heat transfer plates in a dry part.

19. The method of cooling by evaporative cooling under item 14, characterized in that additionally

j) form channels (3, 4) in a dry gap between adjacent plates and send them in a fluid medium product flow and workflow, while the product stream separate from the workflow; and

k) form the channels (5) in the wet gap between adjacent plates, and the wet channels of the gap should not be parallel to the channels of the dry gap, and send to them a working stream after it passes through the perforation.

20. The method according to p. 19, characterized in that the channels on the dry sides of the plates oriented parallel to the side of the plate closest to the perforation.

21. The method according to p. 19, characterized in that the channels on the wet sides of the plates are oriented in the direction of the nom, than parallel to the guides on the dry side.

22. The method according to p. 19, characterized in that it further distribute the liquid to wet the plates through the wicking layer (7) on the wet side of the plates.

23. The method according to p. 22, characterized in that it additionally creates a layer on the dry side of the plates, which is impervious to the evaporating liquid.

24. The method according to p. 19, characterized in that additionally satisfy the perforations (11) plates for directing the work flow through the perforations from the dry side to the wet side and further flow through the damp side.

25. The method according to p. 24, characterized in that it further form a boom (12)having a size and configuration to help prevent output of the working flow of the evaporative cooler before the expiration of the flow through the perforations.



 

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FIELD: heat engineering.

SUBSTANCE: method comprises making conical flanges on the plate and drilling temporary opening in the plate. The flanges are made by means of multiple extruding with removing the bottom of the flanges. The temporary opening is drilled after the first extruding. The surface of the plate is rifled.

EFFECT: enhanced reliability.

4 dwg

FIELD: heat power engineering, machine engineering, possibly manufacture of members of heat exchanges or reinforcing members.

SUBSTANCE: ribbed sheet panel includes base made of metallic sheet and having outer ribs welded to base by action of HF-currents. Base has protrusions on its rear side. Relation of protrusion height to thickness of base is in range 0.8 - 2.0. In order to make such panel, cylindrical blank of metallic sheet being base of panel is shaped to helix. Ribs are welded by means of HF- currents to outer side of base along helix. Then ribbed panel is developed till predetermined curvature radius. On rear side of panel base protrusions are made by pressing-in ribs at process of their welding to outer side of base and(or) by forming.

EFFECT: enhanced operational characteristics of panels.

8 cl, 2 ex

FIELD: applied in heating systems.

SUBSTANCE: the heating panel has an upper and lower plates formed integral opposite each other with formation of an inner passage for fluid, a great number of coupling components, each passing symmetrically from the upper and lower plates in the direction of the lower and upper plates respectively and connects the upper and lower plates to each other, inner passage for fluid formed inside the plate with the aid of the great number of coupling components, and two coupling sections for supply and discharge of hot water, one or more coupling components, and two coupling sections for supply and discharge of hot water, one or more coupling components near the coupling components are perforated with formation of holes. The holes are filled with fused plastic resin, and fused plastic resin forms a single piece with the coupling components with the aid of pressure.

EFFECT: provided a change of the direction in which the panel cracks spread, improved strength of the plane of joint in the changed direction thus improving the panel resistance to pressure.

2 cl, 4 dwg

FIELD: heat engineering, namely plate type heat exchangers.

SUBSTANCE: heat exchanger includes pack of plates. Each plate has at least one row of flanged round openings whose flanges are inserted in respective opening of adjacent plate for forming duct for passing one of media through heat exchanger. Flanges of round openings are cone ones and they have outlet cylindrical portion and constant-thickness walls. Height of cylindrical portion consists 0.25 - 0.3 of flange height; cone surface of flange is joined with plate by means of curvilinear surface whose bending radius in longitudinal section consists 7 - 7.5 of plate thickness values. On surface of plate spherical convex zones are formed with height consisting 3 - 4 of thickness values of plate; spacing between axes of said zones is in range 20 - 30 thickness values of plate.

EFFECT: improved process for making heat exchanger due to selection of optimal configurations of flanges and sizes of plates including dimensions of flanged openings of plates.

3 dwg

Cooler // 2263865

FIELD: computerization engineering; cooling heat-liberating electronic components of computers.

SUBSTANCE: proposed cooler is made in form of plate stack provided with coolant supply and discharge passages; plate stack consists of plate-base made from material possessing high heat conductivity and plate-cover consisting of at least one part; inner surface of plate base has recesses; plate-cover has coolant passages made in form of bow-shaped cavities which are located from its outer diameter towards center in such way that walls of passages extend to upper plane of plate-base and cross recesses made in it.

EFFECT: simplified structure; low cost of manufacture; enhanced efficiency of heat pick-up from computer elements.

5 dwg

Air cleaner // 2262455

FIELD: mechanical engineering.

SUBSTANCE: invention relates to ventilation and air conditioning systems for vehicle cabins and/or rooms of stationary objects and is designed for cleaning air from harmful impurities. Proposed air cleaner designed for cleaning air from gaseous impurities contains unit built into ventilation system and consisting of ultraviolet radiation source and photocatalytic element in form of at least one packet, both arranged in housing. Packet of photocatalytic element is made up of separate thin-walled plates with two-side longitudinal projections on their surfaces arranged at a distance for relative contact by tops in adjacent plates of packet to form channels for passing cleaned air. Novelty is that two-side projections of each plate in packet are made in form of rigid ribs, triangular in section, tilted at angle to on-coming flow of cleaned air and intersecting in space relative to each other at opposite sides of plate. Plates in packet are installed with possibility of intersection of ribs of adjacent plates. Projections can be made in form of fan-like arms diverging on one side of plate and converging on the other side.

EFFECT: improved efficiency of air cleaning, provision of resistance of packet of photocatalytic element to vibration loads, reduced labor input in manufacture.

2 cl, 5 dwg

FIELD: gas turbine construction.

SUBSTANCE: matrix can be used in heat exchangers of heat regeneration heat system's exchanger, as well as for warming up (cooling down) gas or liquid in different heat-sing installations. Matrix of ring-shaped lamellar heat exchanger has heat-exchange members formed by lamellar plates with corrugated parts and openings of collectors, which are connected by means of lugs of internal and external diameters of plates or by means of lugs of collectors. Corrugated parts and collectors are limited by internal and external diameters of ring-shaped plate, or by lines being equidistant to them, and by frontal planes being parallel to axis of symmetry of corrugated parts. Axes of symmetry of any part and of collectors pass through center of plate. Angles between frontal planes of distributing and gathering collectors are equal to each other. Vertexes of angles are disposed at concentric circles having the same or different radiuses. Area of distributing collector relates to gathering collector is directly proportional to relation of corresponding radiuses of vertexes of angles and belongs to 0,4-0,8 interval.

EFFECT: improved efficiency of operation of heat exchanger.

2 cl, 7 dwg

FIELD: agriculture: heat engineering equipment for poultry and stock-rearing.

SUBSTANCE: the invention is dealt with the field of agricultural heat engineering equipment ensuring a heat transfer from one heat-exchanger to another in presence of aggressive corrosion-influencing components in one of them. The equipment may be used in the gas-air ventilation facilities of heat recovery in poultry and stock-rearing farms. The method of production of a cross-running heat exchanger out of a polymeric material containing a package made out of polymeric cellular plates bound to each other and encased in a box ensuring an inlet and an outlet of warm and cool air streams. At that the cellular plates located in one direction in a package are bound to each other by a two-sided polymeric adhesive tape through gaskets made out of the same polymer and placed along the surface and perpendicularly to directions of cells in a plate, are kept till full polymerization of the joints with following formation of the package on all its corners with metal angle sections into a rigid metal framework. At that in one of the vertical sides of the angle section they drill some bores ensuring a free running of a liquid. Then using a sliding fit the package is inserted in the guides made out of the angle sections and mounted perpendicularly to the corners of the air-distributive box so, that the bores of the lower corner of the package meet the bores of a lateral wall of a guide. The package is fixed in the guides formed by the metal angle sections. The bores of the lower angle section of a guide should be located opposite to the bores drilled-in in the lower wall of the air channel of the box placed above a draining container. The invention ensures the necessary tightness of the channels linking the heat exchangers, possibility to use the heat exchangers at low temperatures and also to increase the cost efficiency of the polymeric material cutting.

EFFECT: the invention ensures the necessary tightness of the channels linking the heat exchangers, possibility to use the heat exchangers at low temperatures and increased the cost efficiency of the polymeric material cutting.

2 dwg

The invention relates to heat-exchange equipment, implements the exchange of thermal energy between the two working environments through the wall, and can be used in ventilation systems and air conditioning for the heat exchange between the supply air and exhaust air

The invention relates to shipbuilding, and directly to the ship exchangers for heating of supply air

The heat exchanger // 2052757
The invention relates to a surface gas-liquid or gas-air heat exchangers, such as a regenerator for gas turbine engines

The heat exchanger // 2047076
The invention relates to a heating engineer, and in particular to heat exchangers, such as radiators, cooling systems of internal combustion engines
The invention relates to heat exchangers in which the channels for the coolant is formed by a plate separating the two media, i.e

FIELD: agriculture: heat engineering equipment for poultry and stock-rearing.

SUBSTANCE: the invention is dealt with the field of agricultural heat engineering equipment ensuring a heat transfer from one heat-exchanger to another in presence of aggressive corrosion-influencing components in one of them. The equipment may be used in the gas-air ventilation facilities of heat recovery in poultry and stock-rearing farms. The method of production of a cross-running heat exchanger out of a polymeric material containing a package made out of polymeric cellular plates bound to each other and encased in a box ensuring an inlet and an outlet of warm and cool air streams. At that the cellular plates located in one direction in a package are bound to each other by a two-sided polymeric adhesive tape through gaskets made out of the same polymer and placed along the surface and perpendicularly to directions of cells in a plate, are kept till full polymerization of the joints with following formation of the package on all its corners with metal angle sections into a rigid metal framework. At that in one of the vertical sides of the angle section they drill some bores ensuring a free running of a liquid. Then using a sliding fit the package is inserted in the guides made out of the angle sections and mounted perpendicularly to the corners of the air-distributive box so, that the bores of the lower corner of the package meet the bores of a lateral wall of a guide. The package is fixed in the guides formed by the metal angle sections. The bores of the lower angle section of a guide should be located opposite to the bores drilled-in in the lower wall of the air channel of the box placed above a draining container. The invention ensures the necessary tightness of the channels linking the heat exchangers, possibility to use the heat exchangers at low temperatures and also to increase the cost efficiency of the polymeric material cutting.

EFFECT: the invention ensures the necessary tightness of the channels linking the heat exchangers, possibility to use the heat exchangers at low temperatures and increased the cost efficiency of the polymeric material cutting.

2 dwg

FIELD: gas turbine construction.

SUBSTANCE: matrix can be used in heat exchangers of heat regeneration heat system's exchanger, as well as for warming up (cooling down) gas or liquid in different heat-sing installations. Matrix of ring-shaped lamellar heat exchanger has heat-exchange members formed by lamellar plates with corrugated parts and openings of collectors, which are connected by means of lugs of internal and external diameters of plates or by means of lugs of collectors. Corrugated parts and collectors are limited by internal and external diameters of ring-shaped plate, or by lines being equidistant to them, and by frontal planes being parallel to axis of symmetry of corrugated parts. Axes of symmetry of any part and of collectors pass through center of plate. Angles between frontal planes of distributing and gathering collectors are equal to each other. Vertexes of angles are disposed at concentric circles having the same or different radiuses. Area of distributing collector relates to gathering collector is directly proportional to relation of corresponding radiuses of vertexes of angles and belongs to 0,4-0,8 interval.

EFFECT: improved efficiency of operation of heat exchanger.

2 cl, 7 dwg

FIELD: mechanical engineering; air conditioning and ventilation.

SUBSTANCE: invention relates to heat exchange devices used in air conditioning and ventilating plants, namely, to methods of evaporating cooling to dew point and to plate devices for evaporative cooling. According to invention, plates of plate device are made so that channels and perforation to pass from dry side to wet side can be at least partially wetted with evaporating liquid. Chute is provided made in part of plates which temporarily holds evaporating liquid in contact with wick material on surface of wet side of plate. Evaporating liquid flows along chute through perforation for liquid into following chute. When chute of plate from wet side is from above, perforation for liquid is on side forming reservoir for wetting opposite wick materials. When flow move along dry side, heat is conveyed to plate. In proposed method several heat transfer plates are used. Said plates have wet and dry sides and they form chutes. Plates are wetted form wet sides with evaporating liquid and they pass separately two flows, namely, working and product ones through dry sides. Flow of working gas passes along dry side and gets through perforation into channels on wet side which is cooled owing to evaporation, thermal conductivity of plate and its heat radiation.

EFFECT: provision of more effective air flow and heat transfer owing to evaporative cooling with intermediate coolant.

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