Heat exchanger

FIELD: heating.

SUBSTANCE: plate-like heat exchanger includes at least one heat exchange plate, and preferably a group of heat exchange plates. At least one of the heat exchange plates includes at least one section having corrugations intended for installation against the corresponding corrugations of the heat exchange plate of the corresponding structure. There are at least corrugations of the first type and at least corrugations of the second type. Location and number of corrugations of the first type and corrugations of the second type is different. Another object of the invention is a heat exchange plate including at least one section having corrugations intended for installation against the corresponding corrugations of the heat exchange plate of the corresponding structure. There are at least corrugations of the first type and at least corrugations of the second type; with that, number of corrugations of the first type and corrugations of the second type is different.

EFFECT: invention allows improving characteristics of a heat exchange plate.

14 cl, 9 dwg

 

The present invention relates to a plate heat exchanger containing at least one heat exchanger plate (preferably several heat transfer plates), and at least one heat exchanger plates includes at least one area having a pattern designed to install flush with the relevant repeatable heat transfer plate to the design. In addition, the invention relates to a heat transfer plate containing at least one site having a corrugation is designed to install flush with the relevant repeatable heat transfer plate of the corresponding structural element.

Modern plate heat exchangers are often provided with plates having so-called pattern "herringbone", i.e. an image with a pattern consisting of straight ridges and grooves. Ridges and grooves change their direction in the center, creating a pattern resembling a Christmas tree. In the heat exchange node that represents a package of heat exchanger plates, the plates are interleaved in such a way that adjacent plates are rotated relative to each other by 180°, so that the ribs intersect each other. Placed thus in the package of heat exchanger plates spaivayut, forming a compact and mechanically stable node of the heat exchanger. Through the use of Teploobmennik plates with a pattern "herringbone" the resulting node exchanger has a specific configuration of channels for a fluid medium through which can flow and exchange of thermal energy corresponding two fluids.

Under pressure (in particular the pressure of the fluid and heat exchanger of the above type deformation plate package, resulting in plates bending moment occurs. That plate could withstand high pressures, for their manufacture are used relatively thick metal sheets, for example, a thickness of 0.4 mm

When run on such plates pattern "herringbone" is undesirable for the material. If you press the stamp made with insufficient accuracy, the plates may have cracks. In addition, due to the large thickness of the plate, you must have high pressure at the pressing stamp.

Fully brazed heat exchanger joints between the plates usually solder with copper solder or solder a copper alloy. Often copper solder (solder a copper alloy) is applied on the metal plate in the form of a coating. Solder is collected at the point of crossing of the riffles. For this reason, size and strength ration is very small.

Fluid which is passed through the heat exchanger with a pattern "herringbone", flows over the crests and robotic down in the grooves, in the result, there are no flows in the form of a continuous straight lines. The front edges of the ridges of the flow velocity is high, while for crests (i.e. riffles) the speed of the fluid flow is low. Thus, the fluctuation of the flow velocity is very high. Where the flow velocity in the heat exchanger is high, is high intensity of heat transfer, whereas where the flow velocity is low, the intensity of heat transfer is small. Therefore, to improve the performance of heat exchangers with the pattern "herringbone", preferably reducing the vibration velocity of the fluid flow.

If flowing through the heat exchanger fluid contains two phases, that is, is a mixture of gas and liquid, repeated change of direction of flow of the ridges and grooves cause the gas displaces the liquid, without allowing it to contact with the plates. Decrease the wettability of the surfaces of the heat transfer plates also reduces the intensity of heat transfer.

Form channels, through which passes the fluid heat exchanger, the plates of which have the pattern "herringbone", also contributes to the large pressure drop of the fluid as it passes through the heat exchanger. The pressure drop is proportional to the work spent on forced flow of fluid through the heat exchanger. Therefore clicks the zoom, a large pressure drop entails a high consumption of energy, in particular, mechanical energy.

The heat exchanger is proposed to solve some of these problems, known from the document US 2007/0261829 A1. This paper proposes a heat exchanger plate with a pattern containing a pattern in the form of protuberances and recesses, between which is formed passing through the heat exchanger channels. Form educated so channels causes a moderate change in the flow rate through the heat exchanger, resulting in a higher intensity of heat transfer. Formed so exchanger plates are collected in the package so that the top plate is rotated so that it faces down deeper (lower part) rest in facing up to the top of the bottom plate. The upper and lower plates spaivayut, forming adhesions, in which the heat exchange plates in contact with each other. However, it was found that during operation of such a heat exchanger may deteriorate the side walls of the protuberances. Obviously, this is a very negative effect on the service life of the heat exchanger.

Thus, the objective of the proposed invention is to provide a plate heat exchanger having improved characteristics in comparison with the known plate-type exchanger is eniami. An additional object of the invention is to provide a heat-exchange plate, in particular a heat exchanger plate for a plate heat exchanger having improved characteristics in comparison with the known heat exchanger plates.

Proposed heat exchanger containing at least one heat exchanger plate, preferably a group of the heat transfer plates, and at least one heat exchanger plates includes at least one area having a pattern designed to install flush with the relevant repeatable heat transfer plate to the design, and there is at least the ribs of the first type and at least one corrugation of the second type, and the number of riffles first type and riffles of the second type is different. Thus the phrase "the number of riffles" can be understood in a broad sense. In particular, the phrase "different number of riffles" may refer to the total number of relevant ribbings on the corresponding heat transfer plate and/or the number of riffles in the specific area of the surface of the heat transfer plate. Thus, in some respects, a different number of riffles can be considered as the density of riffles, expressed, for example, as the number of riffles matched with the appropriate type per unit area. As mentioned above, the phrase "the number of riffles" can only refer to a particular section of the heat transfer plate, and this "plot", as a rule, must have a certain size, in particular, should be chosen in such a way that when you change the size of the area by a certain amount, by summing and averaging the number of riffles per unit area will be more or less constant number. In particular can choose more or less is preferable in terms of number and/or density) of riffles, the surface area of the heat exchange plates. For example, near a hole for the entrance and/or exit of fluid figure exchanger plates are often different from the "standard picture". The results of the assessment of an appropriate number of holes will be better if such "non-standard parts not taken into account. The phrase "different number" riffles essentially you can understand any deviation from unity of the ratio of the number of relevant riffles. For example, the ratio may be as follows: ≥1,05, ≥1,1, ≥1,2, ≥1,3, ≥1,4, ≥1,5, ≥1,6, ≥1,6, ≥1,75, ≥2, ≥2,25, ≥2,5, ≥2,75, ≥3, ≥3,25, ≥3,5, ≥3,75, ≥4, ≥4,25, ≥4,5, ≥4,75 and/or ≥5. Preferably for this relationship choose a natural number. Of course, can also use the values back against proposed the values. With regard to differences between the ribbings of the first type and the ribbings of the second type (and possibly even repeatable third, fourth, fifth type, and even more types), then essentially this difference may be implemented in any way. For example, roughening of different types may differ in size, surface area, shape (e.g., parallel to the surface of heat transfer plate and/or perpendicular to the surface of the heat transfer plates, the material, surface treatment, surface treatment, thickness of the heat transfer plate at the location of riffles or near them, the orientation of the pattern (e.g., up and/or down and/or slope), the angular positioning of the respective ribs and other similar parameters. The possible combinations of two or more of the above signs riffles. In addition, under the "wavy", not necessarily understood to be actively forming area of the heat exchange plates. Instead, the corrugation may be formed through the active molding (for example, by stamping and other similar operations) sites, located next to the corrugation. In addition, the term "corrugation" can also be understood in a very broad sense. For example, the corrugation can be a protrusion, a recess, a groove, a protrusion, a recess, beveled the second edge, jumper and similar items. As it usually happens in the case of plates for plate heat exchangers, two adjacent plates adjacent to each other can have a different orientation. In other words, the plate heat exchanger can mainly consist of two differently spaced heat transfer plates having a corresponding pattern of riffles, and reefing going up in contact with the respective ribs of the respective heat exchanger plates going down. Although in principle for manufacturing such a plate heat exchanger, for example, can produce two heat exchanger plates (or more plates) various designs, usually design and make only one heat exchanger plate, and the two aforementioned different "designs" heat transfer plate to receive, turning every second plate package of heat exchanger plates through 180°. Of course, to ensure effective closure of a heat exchanger unit, the top plate and the bottom plate typically has a different design. Mainly used for this essentially flat metal sheets. After Assembly of the package of heat exchanger plates (and, depending on the circumstances, other components) such a "blank" plate heat exchanger is usually passed through a tunnel oven to Spa shall be the appropriate components and to form a compact and mechanically strong, heat-exchange site. Of course, the plate heat exchanger (essentially) can only have a roughening of the above two different types. However, also may include roughening three, four, five or even more different types. We offer plate heat exchanger (as any heat exchanger) must have two separate groups of channels for the fluid, which are separated from each other in a fluid environment. The reason for this device is that thermal energy must be transferred from one fluid to another. In rare cases, in the same heat exchanger is used, a greater amount of fluid and, consequently, a greater number of separate channels for the fluid. Usually two (or even more) fluid have different characteristics. So two different fluids can have a different state of aggregation (for example, one fluid may be a liquid and the other gas). One or both fluids may also be a mixture of gas and liquid, with different ratio between gas and liquid. In addition, two different fluids typically have different temperature (at least at the inlet block heat exchanger) and/or different pressure. Moreover, different fluids can have different viscosity, different density, different heat capacity and other parameters. P is imanae different number (density) of the ribbings of different types, can a simple way to ensure mechanical strength, different for the two different channels for the fluid containing two different fluids. Thus, the mechanical strength of the plate heat exchanger may remain at the same level or even increase, while the dimensions of the block of the heat exchanger can be reduced. For example, if the ribs of the first type are "responsible" for connection with the upper heat transfer plate, and the ribs of the second type of connection with the lower heat transfer plate, providing a different number of riffles first and second types can ensure adaptation to mechanical stability, on the one hand, between "middle" and "upper" plate and, on the other hand, between "middle" and "lower" plate to the pressure corresponding to the fluid flowing through appropriate channels.

In addition, using the proposed design can be a simple way to get the channels of two different types for two different fluid environments. For example, channels of different types can have different cross-sectional areas (in particular the shape and/or size), the curvature of the corresponding channel for the fluid, the number of "obstacles" (for example, producing vortices) and/or other parameters. Thus, you can obtain the exchanger with the most preferred PA what ametramo. For example, such a heat exchanger can be improved dimensions and/or increased service life and/or better performance.

In particular, the plate heat exchanger can be constructed so that the ribs of the first type and the ribs of the second type had a different design and/or different size. Using this embodiment, in particular, can easily provide different strength of the corresponding compounds (for example, to accommodate different pressure of the respective fluid) and/or the size and/or characteristics of the channels for the fluid formed between the respective connections, so that they match the characteristics of the corresponding fluid. The expression "different design" may be understood in a broad sense. "Different design" can refer not only to the size and/or shape of the respective ribs (especially if you watch the corresponding heat transfer plate on the top and/or bottom). For example, different design (in particular the size and/or shape) may also relate to the cross-section of the corresponding structure. Moreover, the proposed invention covers more different "designs", including, for example, varying the thickness of the corresponding heat is bonneu plate on the corresponding section, different material, different coating material, different surface treatment and/or similar.

It may be preferable that the plate heat exchanger was designed so that the ribs of the first type and the ribs of the second type have different shapes. Under the "form" of the corresponding corrugation is in particular possible to understand the form you see when observing the corresponding heat transfer plate on the top and/or bottom. In particular, the use of different forms for ribbings of different types may be appropriate if, as a result of choosing different forms of the compounds and/or the resulting channels for the fluid will be a good fit for the parameters of the applied fluid. For example, using the ribs of the first type of the first form, can achieve very low hydraulic resistance used in the first heat exchanger fluid. Applying a roughening of the second type different forms, can achieve a higher hydraulic resistance used for the second fluid. This higher hydraulic resistance causes additional turbulence. Additional turbulence can increase the intensity of heat transfer from the corresponding fluid medium to the channel wall and, eventually, to another fluid. Thus, more than in the high resistance can be used to increase heat transfer increasing, thus, the performance of the finished heat exchanger. In addition, the combination of the same forms and different shapes can be applied, in particular, if there is a pattern of the third, the fourth type (or even more types of riffles). Also can perform multiple exposure by selecting the appropriate combination of the number of riffles and form riffles.

However, it may be preferable that the plate heat exchanger was designed so that the ribs of the first type and the ribs of the second type essentially have the same shape. In particular the implementation of the ribbings of the same shape may be preferred to the corresponding form had some (preferred) characteristics, for example, particularly low flow resistance, particularly high mechanical strength, particularly preferred ratio between the area and length of edges, and other similar characteristics.

In particular, the heat exchanger can be constructed so that at least the ribs of the first type and/or at least one corrugation of the second type have, at least partially, an elliptic shape, a circular shape, teardrop shape, a polygonal shape and/or symmetrical polygonal shape. During the first experiments with these forms had the camping especially preferred. In particular, when using elliptical and/or circular shape could be obtained particularly high mechanical strength, especially long service life of the resulting compound and/or a particularly large surface connection, if to compare with line bounding the surface of the joint, in combination with relatively low hydraulic resistance. Teardrop shape usually entails a particularly low flow resistance, thus reducing the losses of mechanical energy. Polygonal shape and/or symmetrical polygonal shape usually leads to the manifestation (mild or moderate) turbulence, which can improve the efficiency of heat transfer. Under symmetric polygonal shape is usually understood as the form in which the majority of sides of the polygon, or even all sides have essentially the same length.

In accordance with another preferred embodiment of the heat exchanger, the number and/or location of at least ribbings of the first type and/or at least ribbings of the second type corresponds to the shape of at least ribbings of the first type and/or at least ribbings of the second type. Applying this kind of symmetry, can get especially durable heat exchanger with a long service life, so that m is a mechanical stress is distributed relatively evenly. In addition, the use of such symmetry results in preferred modes of the flow of the fluid, which reduces the hydraulic resistance and/or increases the efficiency of heat transfer.

In accordance with another variant of the heat exchanger, at least the ribs of the first type and/or at least one corrugation of the second type is made, at least partially, so that they have essentially flat upper and/or lower surface. With such a flat surface bonding strength of such a pattern with the corresponding corrugation of adjacent heat exchanger plates can be very high, at the same time conserve solder (for example, copper solder and/or solder a copper alloy).

In accordance with another preferred embodiment of a plate heat exchanger, at least the ribs of the first type and/or at least one corrugation of the second type are located, at least partially, along straight lines, and these straight lines are preferably arranged at an angle to the side edge of the respective heat transfer plate. Using this arrangement riffles, can get a simple, yet effective design of heat exchanger plates. In particular, for getting ready a plate heat exchanger can apply the heat the second plate is essentially only one type, turning every second plate package of heat exchanger plates by 180° relative to the respective adjacent heat transfer plates. Thus, you can save on tools and warehouses, accordingly reducing the cost of manufacture. Straight lines are preferably at an angle of approximately 45° to the corresponding lateral edge of the respective heat transfer plate. However, there are certain deviations from this preferred angle. For example, the interval of possible angles may begin with 30°, 35°, 40°, 42°, 43° and/or 44° and end 46°, 47°, 48°, 50°, 55° and/or 60°. Despite this, the invention in its most General embodiment, its implementation is not limited by any of these angles.

In accordance with another preferred embodiment of a plate heat exchanger, at least the ribs of the first type and/or at least one corrugation of the second type are located, at least partially, so that at least some portions of at least one of the circulating fluid is directed along a curved path. Normally, therefore, can increase the heat flux corresponding to the flowing fluid, thereby enhancing the performance of the heat exchanger.

Additional or alternative heat exchanger can skonstruiroval is so, at least the ribs of the first type and/or at least one corrugation of the second type are located, at least partially, so that at least in some sections is formed of at least one rectilinear channel for at least one of the circulating fluid. With this design can usually reduce the hydraulic resistance. Thus, it is possible to obtain savings of mechanical energy. This design is particularly applicable in the case of a fluid, having a particularly high and/or very low viscosity and/or in combination with such a design plate heat exchanger, in which the turbulence creates other means.

In addition, it is proposed to construct a heat exchanger so that at least the ribs of the first type and/or at least one corrugation of the second type are located, at least partially, so that at least in some sections formed at least one channel to at least one of the circulating fluid flowing parallel to at least one of the side edges of the respective heat transfer plate. Thus, usually can get a particularly preferred fluid flow between the inlet pipe and outlet pipe of the corresponding channel for the fluid.

In accordance with the laws the AI with another preferred embodiment of the heat exchanger, at least one of the heat transfer plates are formed at least partially from a metal sheet and/or sheet of metal alloy, and this plate preferably contains, at least in some areas, the coating made of an adhesive, preferably of solder. The metal plate can be manufactured, for example, aluminum, aluminum alloy, iron, copper, metal alloy (e.g. steel), copper alloy and other similar materials. As the adhesive can be applied adhesive or similar means. Of course, can also apply the solder (or hard solder, for example, copper or copper alloy. It should be noted that this proposed sign may be regarded as developmental signs restrictive part of the original claim 1.

In addition, the present invention proposed a heat-exchange plate containing at least one site repeatable designed to install flush with the relevant repeatable heat transfer plate of the corresponding structural element having such a construction, in which there is at least the ribs of the first type and at least one corrugation of the second type, and the number of riffles first type and riffles of the second type is different. Such heat-exchange plate especially suitable for office is for manufacturing a plate heat exchanger of the above type. In addition, the proposed heat transfer plate may have the same characteristics and advantages described above in connection with the site of the heat exchanger, at least similar. In addition, the heat transfer plate may be subject to modifications in the above sense, at least similar.

Further, the invention and provide them with the advantages explained in detail in the examples of embodiments of the invention described below with reference to the accompanying drawings showing the following :

Figure 1. Schematically shows a top view of a heat exchanger plate for a plate heat exchanger in accordance with the first embodiment of the invention.

Figure 2. Schematically shows a side view of the heat exchanger plate of figure 1

Figure 3. Schematically shows a side view of several heat exchange plates 1 and 2 are collected in the package.

Figure 4. A perspective view schematically shows a heat exchanger in accordance with a typical embodiment.

Figure 5. Schematically shows a top view of a heat exchanger plate for a plate heat exchanger in accordance with the second embodiment.

6. Schematically shows a side view of the heat transfer plate in Figure 5.

7. Schematically shows a side view of several heat transfer plates, 5 and 6, collected the filled.

Fig. Shows a typical path of the fluid flow plate heat exchanger containing a heat transfer plate in accordance with a variant embodiment of the invention in Figure 5-7.

Plate heat exchangers (9), such as, for example, a heat exchanger, shown in figure 4, are known devices for transferring heat between two different fluid environments. Plate heat exchangers (9) have different applications and uses, for example, in the automotive industry, as well as for cooling and heating of buildings and in other similar applications.

Plate heat exchanger (9) contains a group established at each other in the package of heat exchanger plates (1, 13). Individual exchanger plates (1, 13) are arranged in a specific configuration of the embossing(2, 3, 14, 15), usually made in the form of protuberances and recesses and/or in the form of ridges and grooves (the latter in particular in combination with a pattern "herringbone"). At the very top and very bottom of the heat exchanger (9) is provided by a flat metal sheet (16) for holding a fluid in a plate heat exchanger (9). Additionally, there are connections (11, 12)for the input (11) and outlet (12) of the two fluid media.

Package of heat exchanger plates (1, 13) are usually produced by installation of heat exchanger layer is (1, 13) to each other and their connection by means of soldering, thus forming a mechanically stable node.

Due to the presence on the heat exchanger plates (1, 13) riffles(2, 3, 14, 15), located in a specific configuration, in the process of soldering are formed separate channels for the two fluid environments, and these individual channels are separated from each other in a fluid environment. Usually two fluids circulate in countercurrent flow between alternating pairs of heat exchanger plates (1, 13). By itself, this technology is well known.

Figure 1 is a top view of a heat exchanger plate (1) in accordance with the first embodiment of the invention, having located in a specific configuration of the ribs (2, 3). As can be seen from Figure 1, figure riffles considered exchanger plates (1), represents a specific configuration of the first protuberances (2) and second protuberances (3), and not widely used at the present time, the pattern "herringbone". In addition, around each of the four corners of the heat transfer plate (1) with round hole (17). These round holes (17) are typical of the connecting elements for the input (11) in the plate heat exchanger (9) and outlet (12) of the plate heat exchanger (9) two different fluid environments. Heat transfer plate (1), depicted in figure 1, the dotted whether the Oia designated area in the form of a square. In the right part of Figure 1 the surface area of heat exchanger plates (1)corresponding to the area shown on an enlarged scale. Due to the increased scale on this drawing clearly located in a specific configuration, the first convexity (2) and the second convexity (3) heat transfer plate (1). As the first concavity (2)and the second convexity (3) protrude to a predetermined height relative to the standard plate (18) in opposite directions. The sides of the protuberances (2, 3) is inclined at an angle of approximately 45 degrees. The molding plate with the above-described configuration of the bumps can be easily done by stamping. In contrast to the pattern "herringbone" configuration of the protuberances (2, 3) in this heat exchanger plate (1) is well suited for stamping process, as it requires a relatively small deformation of stamping plates. Due to this it is possible to significantly reduce the risk of cracks in the heat exchanger plate (1).

The first convexity (2) and the second convexity (3) form the first pattern of the first bumps (2), and a second pattern of second protuberances (3). In this embodiment, heat exchanger plates (1) first convexity (2) and the second convexity (3) have an essentially flat first vertex (4) and second flat tops (5) with the first surface of the d and the second surface respectively. As follows from Figure 1, the surface of each of the first vertex (4) of the first protuberances (2) lower surface each second vertex (5) of the second bumps (3). As the number of first bumps (2) and second protuberances (3) are essentially the same, the total surface (4) of the first vertex of the first surface (2) is also less than the total surface (5) of the second vertex of the second surface (3).

During manufacture of the heat exchanger (9) of several heat transfer plates (1) heat exchanger plates (1) are combined so that, for example, the first surface (4) of one plate (1) rigidly connect (soft solder or hard solder, glue) with the first surfaces (4) bottom plate (1), similarly, the second surface (5) of one plate (1) rigidly connect (soft solder or hard solder, glue) with the second surface (5) of the upper plate (1) (as shown, for example, 3). Due to the relatively large areas of the first surfaces (4) and second surfaces (5) in this embodiment of the invention receives a relatively strong connection. Figure 3 shows the connection (10) of material between two adjacent first surfaces (4) and two adjacent second surface (5), respectively. Such a connection (10) materials can be created using any known in the art of process, voltage is emer, by soft soldering or hard soldering, gluing, and other similar operations.

During operation of the heat exchanger (9) filled with pressurized fluid environments (and the two pressure applied fluid may be different), resulting in a trend towards the separation of the heat transfer plates (1). In addition, the heat transfer plate (1) can be expanded due to higher temperature fluid. Due to the pattern formed of the first and second protuberances (2, 3), all stresses in the material of the plate is directed essentially in the direction of the plate material, therefore, if in this case and are bending moments, it is small. The absence of bending moments increases the strength and service life of the structure. In addition, durability of the heat exchanger (9) is increased due to the relatively large surface areas (10) of contact between the first and second protuberances (2, 3). Due to this increase of strength for the manufacture of heat exchanger plates (1) can use thinner sheet metal. Alternative can apply conventional sheet metal thickness of 0.4 mm, while the burst pressure of the heat exchanger (9) will be 600 bar, while in the case of a standard heat exchanger with a pattern "herringbone" similar pressure is 200 is ar.

Figure 2 shows a side projection of the first (2) and second (3) bumps along the lines a and b, denoted by, respectively, the dashed and solid lines.

The heat exchanger (9), proposed in accordance with the invention, provides for the possibility of adaptation of the opposite sides to different pressures of the fluid, as is often required.

Giving the first (2) and second (3) convexities such a form that they have different surface area (first (4) and second (5) the surface), can provide different flow settings (which affect the pressure drop of the fluid on two sides of each plate (1) and, therefore, these parameters can provide different settings for the two applied fluid. In addition, due to the size of the zones (4, 5) contact of two adjacent plates (1) (area (4, 5) contact is connected through the connection (10) materials) may be a heat exchanger (9), in which the resistance to pressure of one fluid is greater than the resistance to pressure of another fluid medium.

Therefore, the prepared heat exchangers (9) can be constructed in accordance with the specific requirements. In particular, the size (both absolute and relative) and the distribution of the first (2) and second (3) bulges can be calculated to provide the desired values of the velocity flux is a and/or pressure drop. At the same time, the size of the zones (4, 5) contact heat exchanger plates (1) can be calculated in accordance with the required strength.

In the form shown in the drawings, the first embodiment of the invention as the surface of the first bumps (2), and the surface of the second protuberances (3) have an oval shape with a long diameter (i.e. the main axis of the ellipse) oriented essentially in the direction of the fluid flow. Thus, the cross section in the direction of the fluid flow is minimized, making it possible to reduce the hydraulic resistance of the fluid (and therefore the pressure drop of the fluid).

First experiments showed that the formation of the flat tops (4) and (5) of the elliptical shape is preferred for the formation of these peaks round shape. Some data indicate that all forms of flat peaks lead to the formation of cracks in the side walls of the first (2) and/or second (3) bulges. While the strength of the connection (10) of material between adjacent heat exchanger plates (1) is strongly dependent on the surface areas of the flat tops (4) and (5), the allowable load on the wall is strongly dependent on the perimeter and thickness of the plate. If the thickness of the plates to change to get the same strength of the walls and compounds (10), it will affect the efficiency of the exchanger is Jena heat exchanger (9). When the elliptical shape of the first (2) and/or second (3) bumps the perimeter easily increase, still leaving the sheet thickness and/or surface compounds (10).

For the sake of completeness it should be noted that, in accordance with an alternative variant of the invention it is also possible execution of the first (2) and/or second (3) bumps any other suitable form. In particular, using the convexity of different shapes, can also increase the perimeters without increasing the area of surface compounds (10).

Figure 3 presents a side view of several heat transfer plates (1), connected with each other by combining (10) materials. The sight of the observer directed parallel to the lines a and b of Figure 1. In the drawing it is seen that the channels (6, 7) have different cross-sections. Channels (6) are larger in size are formed of heat exchanger plates (1) between the first protuberances (2) with the first vertex (4), having a smaller surface. Of course, due to the connection between the first peaks (4) smaller size provided a weaker connection than the connection between the second peaks (5) larger. In addition, between the second protuberances (3) formed by the second channel (7) smaller. However, due to a stronger mechanical connection (10) between the second peaks (5) larger provided the opportunity to use the Oia second channel (7) is smaller under the fluid, under higher pressure.

In accordance with the embodiment of heat exchanger plates (1), which is shown in Fig.1-3, first (2) and second (3) bulges are located symmetrically in a rectangular grid, with the first (2) and second (3) convexity located at every second grid point. Thus, they are alternating with each other along several parallel lines, and intervals between the first (2) and second (3) bulges are equal intervals between the parallel lines is also the same. In this case, the channels (6, 7)formed for fluid, follow essentially along the zigzag line. In other words, the corresponding fluid medium compelled to flow along the crests and grooves, as in the case of the pattern "herringbone". Instead, only its collision with rounded "pillar" tapering channels formed first (2) and second (3) bulges at the point of connection (10) between the collected package of heat exchanger plates (9).

Naturally, the presence of the first (2) and second (3) bumps will continue to cause certain changes in the value of the velocity of the fluid flow and direction, as well as some turbulence in the fluid. However, to eliminate turbulence completely in most cases Nigel the tion, because the normal laminar flow of a fluid medium inherent lower the intensity of heat transfer. Using the proposed configuration of the location of the protuberances (2, 3) get the change in heat flow in a fluid environment - from weak to moderate changes. Thus, for a given average velocity of the fluid flow in the heat exchanger (9) reaches a lower pressure drop per unit of heat transferred. Therefore, also reduces the consumption of mechanical energy required to move the fluid through the heat exchanger (9), per unit of heat transferred, in particular in comparison with heat exchangers having the pattern "herringbone".

To improve the characteristics of the fluid flow first (4) and second (5) flat upper surface positioned so that their greatest diameters (major axis of the ellipse) essentially take place in the direction parallel to the direction of the fluid flow in the heat exchanger (9). The direction of flow in the heat exchanger can be defined as the local direction of the main fluid flow, averaged over the many bumps (2, 3).

However, they can also be positioned so that their maximum diameter is at any angle to the direction of the fluid flow in the heat exchanger (9), and even to have different angles that change is on the surface of the heat transfer plates (1). In addition, there is a possibility due to a change in size and/or shape of the first (4) and/or the second (5) the upper surface to modify the surface of heat transfer plate (1), which leads to local changes in individual and/or the relative characteristics of flow and pressure.

In accordance with a particularly preferred embodiment, the orientation of greatest diameter varies from essentially perpendicular direction to the parallel direction relative to the straight lines connecting the hole for the input (11) and air outlet (12) of the fluid. This arrangement facilitates the distribution of the fluid entering through the inlet (11) for the fluid across the entire width of heat exchanger plates (1) and again contributes to the fact that fluids coming from the side parts of the heat transfer plates (1)are directed to the outlet (12) for the fluid.

As shown in Figure 3, the first (6) and second (7) channels, in particular the respective centers of the first (6) and second (7) channels, have a period of (8) with a straight, essentially unperturbed by the lines of flow of the current environment.

In this case, for example, fluid in the second channel (7) not have to change its direction due to the proximity of the top of the first vertex (4). However, for the fluid to a certain extent influenced by the proximity of lavahi right vertex (5). If the fluid in the heat exchanger (9) with channels (7) of this type use two-phase fluid environment, that is, the fluid which is a mixture of gas and liquid, the gas phase tends to flow along the gap (8) in the center of the second channel (7). This means that the gas can flow through the heat exchanger (9) has no negative impact on the wetting of the walls of the heat exchanger plates (1) the liquid phase of the fluid. Thus, as heat rises. Similar reasoning applies in the case of the first channel (6).

In some cases, operation instead of surface evaporation on the walls of heat exchanger plates (1) may occur nucleate boiling. This nucleate boiling can occur in particular in the recesses, in which the flow rate is significantly reduced. The presence of nucleate boiling even more increases the intensity of heat transfer.

In an alternative embodiment of the invention, not shown in the drawings, the first (2) and second (3) convexity located in the grid is symmetrical, but unlike the case for heat transfer plate (1) in accordance with Figure 1-3, this grid is designed so that the resulting channels (6, 7) are parallel to the edges of the heat transfer plate (1). This arrangement tends to reduce the pressure drop is Oia, at the same time reduces the heat transfer, so as vertices (4, 5) occluding each other.

However, there are essentially any modifications to this location. In particular, the figure does not have to be symmetric across the plate. Thus, in order to direct the flow of the flowing fluid to the appropriate path and to control the turbulence and pressure drop, we can use a different configuration of the location of the bumps.

In addition, the pattern formed by the first (2) and second (3) bulges (and perhaps even more protuberances of different types - not shown) does not need to cover essentially the entire heat exchanger plate (1). This figure can be combined with deflecting baffles and deflectors with very flat surfaces and, if required due to any reasons, with the usual drawings "herringbone".

Figure 5 is a top view of the heat exchanger plates (13) in accordance with the second embodiment. Such heat exchange plate (13) can be used for manufacturing a plate heat exchanger (9), shown in Figure 4. This second variant embodiment of the invention somewhat similar to the first variant implementation of the heat transfer plate (1), depicted in figure 1-3. However, and this is the version location the number and shape of the first (14) and second (15) convexity different.

In this embodiment, heat exchanger plates (13) the first concavity (14) are essentially hexagonal shape, while the second concavity (15) have an essentially triangular shape. Similar to the first variant implementation of the heat transfer plate (1) as the first (14)and second (15) the convexity of the considered heat exchanger plates (13) are the first vertex (19) and, accordingly, the second node (20) is essentially flat upper surface. From Figure 5 it is seen that the surface area of one of the first peaks (20) (first concavity (15)) is greater than the surface area of one second vertex (19) (second concavity (14)).

The location of the first (14) and second (15) convexity relative to each other is selected to meet individual forms the first (14) and second (15) of the bumps. As the first concavity (14) have the form of a hexagon, the second concavity (15) are also located within the hexagonal form (22), around the Central first (14) convexity. Therefore, there are six second protuberances (15)located around each of the first concavity (14). Similarly, as the second concavity (15) have the form of a triangle, the first concavity (14) are also located within the triangular form (21), around a Central second (15) convexity. Sledovatel is, there are three second concavity (14)located around each of the second concavity (15).

In this embodiment of the invention, the first (14) and second (15) convexity located so that the angle of the hexagonal first concavity (14) is directed toward the second triangular convexity (15). In contrast, the straight line of the triangular second concavity (15) "directed" towards the first hexagonal protuberance (14). To provide this arrangement, the second concavity (15) are placed so that they change direction along the line (C), as shown in Figure 5. In the first experiments demonstrated that thanks to this arrangement reduced mechanical stresses in the sheet metal heat transfer plate (13) with changing pressure and/or temperature of at least one of the fluid. Therefore, in most cases it is possible to increase the service life of the resulting heat exchanger (9). In addition, the proposed location of the first (14) and second (15) of the bumps in the first experiments showed relatively good intensity of heat with a relatively low mechanical power loss or pressure drop of the fluid.

However, in the case of other fluid and/or other characteristics of the fluid may be preferred another location PE is o (14) and second (15) bumps and/or other alignment of the first (14) and second (15) of the bumps. In particular, choosing the appropriate location and/or alignment of the first (14) and second (15) of the bumps, the heat exchanger (9), made of the proposed plates (13), can be adapted to your specific requirements.

Figure 6 shows the lateral projection of the first (14) and second (15) bumps along lines (C) and (D), which are indicated respectively dashed and solid line. Due to the different number and/or shape and/or size of the first (14) and second (15) the protuberances on opposite sides of the heat exchanger plates (13) can provide different flow characteristics and/or pressure due to the formation of different number, shape and size of the "obstacles"faced by the fluid on its path through the heat exchanger (9).

It should be noted that the drawings are conventional image on which side projections are depicted by straight lines, although in most cases it is not. Shows "straight" line in most cases have curves, and a lateral projection in the reality usually does not form the "corners".

7 shows the location of several of heat exchanger plates (13)installed in the package on top of each other and connected to each other by means of connection (23) of the materials. This figure shows the side view of such a package of heat exchanger plates (13), when viewed in n the Board parallel lines (C) and (D), shown in figure 5. Therefore, figure 7 shows the "two levels" of the heat exchanger (9). From Fig.7. it is seen that in accordance with the description of the second variant of the invention, the first channel (24) of a larger size are between less numerous second protuberances (15).

Similarly, the second channel (25) of smaller size located between the first protuberances (14), more numerous than the second concavity (15).

It should be noted that the total strength of the connection between the two heat exchanger plates (13) is determined not only by the surface area of the first peaks (19) and/or the second nodes (20) of the first protuberances (14) and, respectively, second protuberances (15), but the relative number of first protuberances (14) and/or the second surface (15). Therefore, increasing the overall strength of the connection between two adjacent heat-exchanger plates (13) by means of second flat tops (20) is smaller compared to common connection with the first flat tops (15) is possible simply by increasing the number of the second flat tops (20). Obviously, thus increasing the overall strength of the connection is possible and with the first flat tops (15).

Due to selection, thus, the total strength of the mechanical connection, possible optimization of the corresponding heat exchanger (9) in otnoshenii.myjsina fluid medium pressure and/or maximum temperature of the fluid, arisen in a particular design. Thus, in particular, it is possible to optimize the performance of the heat exchanger and the appropriate sizes of the heat exchanger (9), and reduced cost of production.

In accordance with the description of the first variant implementation of the heat transfer plate (1), which is shown in Fig.1-3, due to the form of the first protuberances (14) and/or the second surface (15), which differs from the circular shape, as shown in the example, where used triangular and hexagonal shape, is provided by the increase in the perimeter edges of the flat tops (19, 20) without increasing the size of the corresponding surface. As a result of such execution design, as already mentioned above, are less susceptible to mechanical damage due to differential pressure and/or temperature changes. Therefore, in particular, ensures the longer service life of the respective heat exchanger (9).

Explore the option of implementing exchanger plates (13) does not preclude the use of the first protuberances (14) and/or the second surface (15)having a different shape, a different number and/or other sizes.

Similarly to the above-described first embodiment of implementation of the heat transfer plate (1), proposed in the second embodiment, heat exchanger plates (13), the first channels (24) Ivo second channels (25) are provided gaps (26) with a straight, essentially unperturbed by the fluid flow, which is also called "lines of sight". In case of "lines of sight", their length largely depends on the specific design of heat exchanger plates (1) with the first (14) and second (15) protuberances, for example, from their relative distance with respect to the length and size of their flat tops (19, 20). Provides performance similar "lines of sight" and in that embodiment of the invention, which is depicted, for example, in figure 3. Here, in the first channel (24), fluid is not forced to change direction due to the proximity of the first peaks (19), it is influenced to some extent by only the second node (20). A similar phenomenon occurs in the second channel (25). When using a heat exchanger (9) with channels (24, 25) of this type with two-phase fluid medium, the gas phase tends to flow along the gap (26) in the center of the first channel (24) or the second channel (25). Therefore, the flow of the gas phase through the heat exchanger (9) has no negative effect on the wetting of the heat transfer plates (13) the liquid phase of the fluid. Thus with improved heat transfer.

Of course, in the case of heat-exchanger plates (13), corresponding to the second variant of implementation (or in the case of the heat transfer plates of razlicnosti) in some cases operation instead of surface evaporation occurs nucleate boiling, in particular in the hollows, in which the rate of fluid flow is significantly reduced. Due to this phenomenon provides an even greater increase in the intensity of heat transfer.

Another property of the proposed plates (1, 13) of the heat exchanger, in particular corresponding to the second variant implementation of the exchanger plates (13), is that the flow characteristics are very different in relation to the direction of the fluid flow due to the layout of the first protuberances (2, 14) and second protuberances (3, 15). On Figa shows the way (27A, 28a), defined in the General direction of the fluid flow, and the dotted curve line (28a) shows the path of the fluid flow on one side of the heat exchanger plates (13)defined by the first surface (14), which are shown in the form of protrusions, while the second concavity (14) is shown in the form of depressions. The solid curve line (27A) similarly indicated path of the fluid flow on the other side of heat exchanger plates (13)defined by the second protuberances (15). Due to deviations in the first protuberances (14) and, respectively, second protuberances (15) along the heat-exchanger plates (13)on both ways (27A) and (28a) is repeated zigzag change the direction of flow of the fluid.

In the direction of the fluid flow perpendicular to the General on the management of the flow of fluid, the flow of fluid of the same obstacles are not met, because the first and second bulges (14, 15) are located exactly along the lines of (C) and (D), as shown in Figure 5, leaving, therefore, the "quiet line" (27b) and (28b) of the paths of flow of the fluid to flow of the fluid essentially without obstacles, as shown in Fig Century At least, provided less resistance to flow in paths (27b) and (28b)than in other directions of the currents.

Such quiet highway (27b, 28b) are preferred because they are superior distribution of the fluid flow on the heat transfer plate (13) and, consequently, across the heat exchanger (9), and consequently, a lower hydraulic resistance in the direction of the fluid flow perpendicular to the General direction of the fluid flow, while the General direction of the fluid flow corresponds to the direction of fluid flow parallel to the long sides of the heat exchanger plates (13). So as in the direction different from a direction passing from the inlet (11) to the outlet (12), the fluid has a lower hydraulic resistance, it is better distributed over the entire heat transfer plate (13).

To the described second variant implementation of the exchanger plates (13) are applicable, at least by analogy, modificat and, described above in relation to the first variant implementation of the heat transfer plate (1), and any modification of the heat transfer plate.

Additional information presented in the application registered by the same applicant in the same patent office and on the same day under the internal registration number 10 01 690. The contents of this application are included in this application by reference.

Item numbers

1. Heat-exchange plate

2. The first bulge

3. The second bulge

4. The first vertex

5. The second peak

6. The first channel

7. The second channel

8. Period

9, the heat Exchanger

10. Connection materials

11. A first connection for fluid

12. A second connection for fluid

13. Heat-exchange plate

14. The first bulge

15. The second bulge

16. Flat sheet

17. Round holes

18. The plane of reference

19. The first vertex

20. The second peak

21. The triangular shape

22. Hexagonal shape

23. Connection materials

24. The first channel

25. The second channel

26. Period

27. The first path of fluid

28. The second path of fluid

1. Plate heat exchanger (9), containing at least one heat exchanger plate (1, 13), preferably a group of heat exchanger plates (1, 13), and at least one of Teploobmen the data plates (1, 13) contains at least one section having ribs(2, 3, 14, 15), designed to be mounted flush with the relevant riffles (2, 3, 14, 15) heat exchanger plates (1, 13) of the corresponding structural element, wherein there are at least ribs (2, 14) of the first type and at least ribs (3, 15) of the second type, and the location and number of riffles (2, 14) of the first type and riffles (3, 15) of the second type is different.

2. The heat exchanger (9) according to claim 1, characterized in that the ribs (2, 14) of the first type and pattern (3, 15) of the second type have a different design and/or different size.

3. The heat exchanger (9) according to claim 1 or 2, characterized in that the ribs (2, 14) of the first type and pattern (3, 15) of the second type have a different shape.

4. The heat exchanger (9) according to claim 1 or 2, characterized in that the ribs (2, 14) of the first type and pattern (3, 15) of the second type have essentially the same form.

5. The heat exchanger (9) according to any one of claims 1 and 2, characterized in that at least part of at least riffles (2, 14) of the first type and/or at least part of at least riffles (3, 15) of the second type have an elliptical shape (2, 3), round shape, teardrop shape, a polygonal shape (14, 15) or symmetric polygonal shape (14, 15).

6. The heat exchanger (9) according to any one of claims 1 and 2, characterized in that the form (21, 22) the location of at least rifle the s (2, 14) of the first type and/or at least riffles (3, 15) of the second type corresponds to the shape of at least riffles (2, 14) of the first type and/or at least riffles (3, 15) of the second type.

7. The heat exchanger according to claim 5, characterized in that, in the case of ribs of the first type and the ribs of the second type have the form of a polygon, the number of riffles first type located around each of the ribs of the second type is equal to the number of corners of the polygon forming the shape of the ribbings of the second type, and Vice versa, the number of riffles of the second type located around each of the ribs of the first type, equal to the number of corners of the polygon forming the shape of the ribbings of the first type.

8. The heat exchanger (9) according to any one of claims 1 and 2, characterized in that at least part of at least riffles (2, 14) of the first type and/or at least part of at least riffles (3, 15) of the second type have essentially flat top surface (4, 5, 19, 20) and/or flat bottom surface(4, 5, 19, 20).

9. The heat exchanger (9) according to any one of claims 1 and 2, characterized in that at least part of at least riffles (2, 14) of the first type and/or at least part of at least riffles (3, 15) of the second type are located along straight lines (a, b, C, D), and the specified lines (a, b, C, D) is preferably located at an angle to the side edge of the corresponding t is ploumanac plate (1, 13).

10. The heat exchanger (9) according to claim 1, characterized in that at least part of at least riffles (2, 14) of the first type and/or at least part of at least riffles (3, 15) of the second type are positioned so that at least in some areas of the heat exchanger, at least one of the circulating fluid is directed along a curved path (27A, 28a).

11. The heat exchanger (9) according to claim 1, characterized in that at least part of at least riffles (2, 14) of the first type and/or at least part of at least riffles (3, 15) of the second Tina are located so that at least in some areas of the heat exchanger is formed of at least one rectilinear channel (6, 7, 24, 25, 27b, 28b) for at least one of the circulating fluid.

12. The heat exchanger (9) of claim 10 or 11, characterized in that at least part of at least riffles (2, 14) of the first type and/or at least part of at least riffles (3, 15) of the second type are positioned so that at least in some areas of the heat exchanger is formed of at least one channel of at least one of the circulating fluid flowing parallel to at least one of the side edges of the respective heat exchanger plates (1, 13).

13. The heat exchanger (9) according to any one of claims 1 to 2, 10 and 11, characterized in that at least one of the exchanger is built of plates (1, 13) formed at least partially from a metal sheet and/or sheet of metal alloy, and this plate preferably contains, at least in some areas of the heat exchanger, a coating of adhesive material, preferably of solder (10, 23).

14. Heat exchanger plate (1, 13)containing at least one portion having ribs(2, 3, 14, 15), designed to be mounted flush with the relevant riffles exchanger plates (1, 13) of the corresponding structural element, wherein there are at least ribs (2, 14) of the first type and at least ribs (3, 15) of the second type, and the number of riffles (2, 14) of the first type and riffles (3, 15) of the second type is different.



 

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The invention relates to heat engineering and can be used in the manufacture of plates of sheet material for heat exchangers pipeless type

The invention relates to heat engineering and can be used in heat transfer equipment such as radiators and air conditioners of automobiles, refrigerators and other heat exchange devices

The invention relates to the processing of metals by adding, in particular, to methods for producing plate heat exchangers pipeless type of sheet material used as radiators, coolers and other designs of heat exchangers

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

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