ES2604533B2 - Heated film heat exchanger and associated procedure. - Google Patents

Abstract

Heated film heat exchanger and associated procedure. The exchanger comprises a plurality of thermal exchange plates arranged in series, and is characterized in that it comprises: a first sealed chamber (29), where a first fluid circulates; a second sealed chamber (30), where a second fluid circulates; removers, called type 1 (24), which describe a rotation movement and are located inside the first chamber (29); removers, called type II (26), which describe a rotation movement and are placed in the second chamber (30); and where at least one of both types of removers, I (24) or II (26), is a remover near the exchange surface. The procedure includes the introduction of at least two fluids in the exchanger, which run through two sealed chambers, and in this process are subjected to the action of two removers.

Description

DESCRIPTION Heated film heat exchanger and associated procedure. OBJECT AND TECHNICAL SECTOR OF THE INVENTION 5 The present invention aims to provide a stirred film heat exchanger and its associated method. It can be used for heating, cooling, evaporation, condensation and concentration of fluids. The film stirring that develops destabilizes the fluid boundary layer, increasing the heat transfer coefficient and reducing the formation of deposits and deposits. The technical sector of the present invention is broad, covering a large number of industries, such as food, where its use as a pasteurizer, chemical or pharmaceutical is contemplated. It is suitable for the treatment of viscous fluids, sewage sludge and wastewater. It is also particularly interesting for the treatment of vapors to condense, both pure and with the presence of incondensable gases. STATE OF THE TECHNIQUE In the prior art prior to the present invention, plate heat exchangers with stirring mechanisms that act from inside the exchanger on one of the process fluids are known. These mechanisms in some cases exert a physical contact on the exchange surfaces, especially useful for removing scale, while in other cases they maintain a separation. The agitation mechanisms exert a turbulence that destabilizes the fluid boundary layer in order to increase the heat transmission coefficient. Examples of heat exchangers of this type are those disclosed in documents WO9725579A1 and EP0521221B1.

The exchangers described in the previous paragraph have the limitation that the agitation mechanisms they possess only act on one of the fluids that pass through the exchanger at a given time. This limitation is due to several reasons. First, all fluids must remain in sealed chambers that avoid mixing with other fluids in other chambers. This property makes it very difficult to find a mechanical solution that allows to generate agitation on more than one fluid without mixing or collision between agitators. In addition, it is very common that in industrial applications the main thermal resistance resides in a single fluid, so that in them it only makes sense to effect agitation on said fluid. 10 However, in those applications in which the thermal resistances of the various fluids are close enough, the exchangers mentioned here lose their original effectiveness. In these cases, the increase in the overall heat transfer coefficient generated by the stirring mechanism is insufficient and does not justify the cost of the investment. In addition, another problem that arises is the formation of deposits or deposits on surfaces bathed by fluids without agitation, which require frequent stops for inspection and cleaning. To solve the problem described in the previous paragraph, US Patent No. 4044824 proposes a plate heat exchanger with 20 stirring mechanisms that act on two fluids instead of just one. To achieve this capacity, the mechanical structure of this exchanger becomes more complex than that of the exchangers with agitation on a single fluid. This greater complexity implies that the probability of breakdowns or breakage of internal components is greater. In this regard, it has the disadvantage of being formed by non-removable structures, which is a major problem in case of breakdowns or breakages. On the other hand, while the agitators help prevent scale, they are never completely eliminated and a manual inspection by operators is necessary every so often, during which the scale layer that exists is manually removed. The invention disclosed in document 4044824 does not disclose mechanisms that allow disassembly to proceed to the inspection of the interior of the exchanger by operators.

Plate exchangers with stirring mechanisms belonging to the prior art prior to the present invention, have a configuration that makes it difficult or impossible for rapid, comfortable and hygienic disassembly of the equipment. It would be desirable that they allow disassembly similar to that applicable to plate heat exchangers without stirring mechanisms, of which the invention disclosed in document EP2674714A1 is an example. The problems mentioned above receive solutions in the present invention. DESCRIPTION OF THE INVENTION 10 The present invention relates to a plate heat exchanger to facilitate thermal transmission between at least two fluids, where each one runs through a sealed chamber that prevents leakage and / or contact with any of the other fluids. This thermal transmission process can, depending on the application, serve to subject the fluids to heating, cooling, evaporation, condensation, concentrate, crystallization, etc. When we use the term “plate heat exchanger” we refer to the one in which the heat exchange surfaces are arranged in accordance with the following basic structure (later possible variants of it will be exposed): a plurality of parallel flat surfaces with each other and perpendicular all of them to the same axis or direction, along which they are distributed maintaining a spacing between each two adjacent surfaces, configured for the passage of a fluid. As variants, the mentioned flat surfaces can have any practicable shape: rectangular, square, circular, polygonal, etc. In a particular embodiment, the spacings do not have to be constant and the plates may not be exactly parallel to each other. In addition, the heat exchange surface may be subject to variations in its roughness and geometry. For example, it can be striated instead of smooth, contemplating all kinds of undulations or channeling through it, regardless of its number, trajectory, depth, shape, etc. In the same way, said surface may adopt a bulge that transforms the original flat surface into a curve, torispheric, ellipsoidal, discoidal, etc.

 Examples of heat exchangers according to the definition given in the preceding paragraph are those disclosed in patent documents EP2674714A1 and EP0521221B1. By way of further clarification, the devices that the person skilled in the art would understand as shell and tube heat exchangers, concentric tubes and spiral exchangers are therefore excluded from our definition of plate heat exchanger. As a synonym for "heat exchange plate", its abbreviated form "thermal plate" is sometimes used herein. And in some cases where there is no room for confusion, it is further abbreviated as "plate", for example by naming "plate heat exchanger". Similarly, "heat exchanger" can be abbreviated as "exchanger." When we mention means of "film agitation with scratching", we refer to those means that exert a physical contact with a certain force on a heat exchange surface. These means may comprise a metal blade, a plastic brush or any other material, etc. They fulfill the double function of removing the inlays that form certain solutes or dispersing components that the fluid carries and substantially increasing the coefficient of heat transfer. This increase is produced by destabilizing the fluid boundary layer in contact with the heat exchange surface. By way of illustrative example, said means, for example a metal blade under the action of a spring, can be fixed on rotating blades, which will be described throughout the document. Scraper mechanisms in exchangers, such as blades or brushes, are widely known in the prior art prior to the present application, therefore no further explanation of them is deemed necessary.

When we mention some means of "film agitation", without making specific mention of scratching, we refer to means that by mechanical action destabilize the fluid boundary layer 30 but do not achieve direct physical contact with the heat exchange surface on the surface. that act In a preferred embodiment, these means are rotating blades that move close to said surface. Distance from

The separation between said means and the exchange surface must be such that it exerts a non-negligible increase in the turbulence on the boundary layer with respect to the turbulence that would be generated by mechanical means of driving away a great distance. An example of remote drive means is a centrifugal pump located several meters from the study point. Particularly interesting, the distance of separation is between 0.25 and 4 millimeters, although separations of up to 30 millimeters and even more are also effective, depending on the fluid to be treated and its rheological properties. Said mechanical destabilization considerably increases the turbulence, thus reducing the thickness of the boundary layer and as a consequence significantly increases the heat transmission coefficient. This phenomenon makes it possible to reduce the size of the heat exchanger, by requiring a smaller exchange surface. In addition, it also minimizes fouling of the same, extending the process times greatly and significantly reducing the frequency of cleaning stops, and in some cases eliminating them. 15 When we affirm that a heat exchange surface has means of “removal away from the surface”, without express mention of film or scratch agitation, we refer to those mobile mechanisms that are different from the two previous cases. As such they are able to give the fluid a kinetic energy that causes a mixture and / or impulse, but that does not cause a destabilization of the boundary layer 20 notable for being sufficiently far from it. An example of such means are blades that are not close to the exchange surface. A distance not close to that may be greater than 30 mm, depending on each fluid and its rheological properties. 25 When we use the term “remover”, without further specification, we refer to mechanical means capable of exerting any of the three effects mentioned in the preceding paragraphs. Thus, a remover will be an element that can exercise film agitation with scratching, film agitation, or removal away from the surface. 30

When we use the term “near surface remover” or its synonym “near surface exchange remover”, we refer to a means

mechanics capable of exercising any of these two effects: film agitation with scratching or film agitation. All removers near the surface are therefore removers according to the previous paragraph. This term is of special relevance in the claims. The title given to the present invention is "stirred film heat exchanger". With this term we refer to that the exchanger has at least 5 a remover near the surface. In this document, the term “consecutive” is used to indicate that two elements of the same type or category are found one after the other, without any elements of the same type interposed between them. In a numerical simile, 10 the numbers 13 and 17 can be considered of the same type, prime numbers, and they are consecutive cousins, because although there are numbers interposed between both, 14, 15 and 16, none of them is cousin. The terms "contiguous" and "adjacent" we use as synonyms. We say that two elements are contiguous or adjacent, whether they are in physical contact or one is immediately after the other, regardless of whether or not they are of the same type or category. Thus, following a simile with the integers, 13 and 14 will always be contiguous. 20 Throughout this document, single and double joints are mentioned. It should be noted that when talking about double joints, it is contemplated that they consist of a pair of elements that are not physically linked together; but by agreement we consider this pair as a single meeting. 25

In accordance with the invention, the present document describes a plate heat exchanger that is traversed by at least two fluids, where each one circulates through a sealed chamber that keeps it tightly insulated from the other fluids. Thus, a number of chambers equal to the number of circulating fluids is available. The exchanger claimed has the particularity that it comprises in at least one of the chambers, some of the following two possibilities: means for film agitation or film agitation with scratching. And in at least one chamber other than the previous one, one of the following three options: means for film agitation, film agitation

with scratching or removal away from the surface. The embodiment of the invention in which removers close to the surface are available, not only in a first chamber of a particular fluid but also in a second chamber for another fluid, is, in the opinion of the inventors, an important novelty for plate exchangers, not known in the prior art prior to the present invention. The reasons for not having previously developed this double system are diverse. On the one hand, in the exchanger the different fluids have to circulate through watertight chambers in such a way that there is no mixing or uncontrolled leakage. The fact of having removers acting simultaneously on more than one fluid complicates the tightness. In addition, complications appear when activating them, because they have to avoid clashes between the mechanisms that transmit them movement. In short, mechanical construction is complex. On the other hand, there is a certain lack of knowledge about a large number of advantages provided by the existence of removers over more than one fluid for certain applications. These advantages are set out below. In most heat exchangers, among the various fluids involved in thermal transfer, it is usual that the thermal resistance exerted by one of them is significantly higher than that of the others. In these cases, destabilizing the film of the most unfavorable fluid greatly increases the overall heat transmission coefficient, while if we act on the most favorable fluid the overall coefficient increases very little. For this reason in normal practice it only makes sense to apply film agitation, with or without scratching, on a single fluid. Otherwise an important complication is introduced in the mechanical construction that entails an extra cost that is not profitable. For example, in an application in which the temperature of a cold and very viscous liquid is raised by means of hot water, acting on the former would considerably increase the efficiency of the exchanger, while the effect of acting on the hot water would be negligible. 30

In any case, there are industrial applications in which the thermal resistance of two opposing fluids is close enough that it is of interest to act on both. Some assumptions of this type are mentioned below, with

illustrative and non-limiting nature. The term viscous fluid refers here to that with a viscosity greater than 50cP: - Heating of a viscous fluid by means of a thermal fluid from a boiler, for example thermal oil. The physical properties of thermal oil, such as density, thermal conductivity, viscosity, etc. They give it a coefficient of film heat transmission much lower than that of fluids such as water, for the same linear velocity. To increase it, the common solution is to boost the oil at high speeds, but since in many heat exchangers the oil circulates through chambers of large cross-section, this is not possible. For example, in a casing and tube heat exchanger, the oil usually circulates through the chamber located outside the tubes, which is of large section. - Heating or cooling of a viscous fluid by means of a residual effluent, such as sewage sludge or water. Such residual effluents usually offer a high resistance to thermal transmission, and this reason often causes them not to take advantage of their energy. - Heating of a non-viscous fluid and with high speed by means of the heat transferred by a condensing vapor. For example, when we condense saturated water vapor to transfer its condensation heat to a fluid consisting of pumped water. In this circumstance, although the coefficient of heat transfer of the first film is going to be higher than the second, the difference is usually not large enough, so that a film agitation in both fluids is interesting. 25

As is known, the resistance to heat transmission by a condensing vapor resides in the liquid condensate layer that forms on the exchange surface. If this layer disappears or reduces its thickness, the heat transfer coefficient greatly increases. In the plate heat exchanger disclosed in this document, this phenomenon is promoted by the film stirring mechanism, 30 with or without scratching. Each time a blade or similar medium passes a few millimeters from the exchange surface, it releases the condensate film from it. The heat transfer coefficient increases until it becomes comparable to the corresponding one

to a phenomenon called condensation in drops. This phenomenon is very desired in certain industrial applications and attempts are made to promote techniques that include chemical agents, surface irregularities, etc. but they are not as effective as a mechanical removal, which physically breaks the film. 5 - Heat exchange by condensing a cooling fluid, such as R-134. The liquid condensate they produce usually has physical properties that make it a much worse heat transmitter than if it were condensing water vapor. In an event in which water is heated by the heat of condensation released by a refrigerant fluid, breaking the condensate film mechanically greatly increases the overall heat transfer coefficient. In this case the effect is much more noticeable than film breakage for condensing water vapor. As in the previous section, an effect similar to that of droplet condensation is achieved. Finally, the claimed heat exchanger is especially effective for handling gaseous mixtures that contain a vapor to condense and in turn there is the presence of incondensable gases. In most industrial applications, when a condensing gas is used to transfer its heat of condensation to another fluid, the gas is treated and purified in such a way that it only contains the expected molecules, and in case of 20 leaks or contamination with Other types of gases, mechanisms are available for their effective evacuation. However, there are applications in which a gas is condensed that will inevitably carry large amounts of other gases of an untiring nature. An example would be multiple effect evaporation systems in the food or wastewater industry. 25

The non-condensable gases are a big problem in the processes of condensation of vapors. On the one hand, as the condensable fraction condenses and becomes liquid, the proportion of the incondensable fraction increases. In a multi-effect evaporation system, for example, it may be necessary to condense a gaseous mixture containing in 95% (m / m) saturated water vapor and in 5% (m / m) a gas non-condensable at operating temperatures, for example methane. As the process of condensation of the mixture progresses, the fraction of water vapor will decrease and the

of methane rising, being able to exceed 50% (m / m). As this assumes that the molar fraction of the water vapor drops, so does its partial vapor pressure and therefore its condensation temperature decreases. This implies a reduction in the heat differential of the heat exchanger, with the disadvantage that it entails. On the other hand, the incondensable gases tend to form a film that is in contact with the condensate layer. This film is a very important thermal insulator that slows down heat transmission considerably. Finally, the incondensable fraction has a strong tendency to accumulate in dead spaces, corners, interstices and areas of lower speed of the exchanger, being very difficult to remove. 10 The disadvantages indicated in the previous paragraph make the condensation of vapors with presence of incondensables very complicated. The exchanger claimed solves all these problems by making these gaseous mixtures as manageable as any other. In addition to mechanically breaking the aforementioned insulating layer, a correct mixture is guaranteed and all dead spaces or susceptible to accumulations of incondensables are effectively swept. In order to evacuate the liquid obtained from the condensation of gases, the claimed heat exchanger contemplates the arrangement of drainage pipes in its lower zones. In a preferred mode, a conduit is arranged between each two adjacent plates 20. In this way the condensates generated are sent to the outside of the exchanger. If the pressure inside is equal to or greater than the atmospheric pressure, these condensates can flow through the ducts due to gravity, without the need for pumping equipment. 25

The heat exchanger object of the present invention is contemplated for the treatment of two or more fluids, each passing through a sealed chamber, and where at least two of said chambers have one or more removers inside. Configurations of plate heat exchangers for handling three or more fluids are known in the state of the art, and in the present invention this possibility is realized in an equivalent manner. As an example, we take a plate heat exchanger where we call the space between two adjoining plates subchamber, with a total of eight subchambers. If we number them correlatively, we can establish a first

camera communicating all the subchambers of the odd positions, in our example they would be numbered 1, 3, 5 and 7. And between the even subchambers, we can communicate the 2 with the 4 and make a second waterproof chamber; and 6 with 8 and generate a third waterproof chamber. The arrangement described so far is applicable to the exchanger claimed herein. 5 In plate heat exchangers known in the state of the art, the usual way of communicating each subchamber with the following is by peripheral conduits, which line the subchambers that interpose between the two outside its perimeter. An important novelty disclosed in this document in one of the embodiments of the invention is the provision of two different types of conduits for this purpose. Consecutive sub-chambers can communicate through peripheral pipes, but the possibility of central pipes is also contemplated. The latter pass through the sinus of the fluid contained in the subchamber or subchambers that interpose between the two subchambers to be communicated. An additional property of the peripheral and central pipes 15 disclosed in this document is that they can be traversed by rotating shafts that provide movement to the different removers. It is contemplated that the central and peripheral pipes described in the previous paragraph are divided into a plurality of sections or segments of pipe. These sections are grouped and conveniently aligned to form the pipes, central or peripheral, of which they are part. It is important to note that the pipes do not have to be continuous along their entire length, but may present discontinuities. For example, in several of the embodiments to be described later, the exchanger is crossed in the center of the plates by means of a central pipe that runs along its entire length. Well, this pipe is divided into a plurality of segments, but where every two consecutive segments are separated by a subchamber. In the embodiments of the invention disclosed herein, four different types of pipes are established: central, peripheral, inlet and return pipes. It is contemplated that all of them are divided into segments / sections. In most situations, reference will be made not to the pipes, but to the segments thereof.

 Each time the term “central segment” appears, it is used as an abbreviation for “segment of a central pipe”. Similarly, every time the term "peripheral segment" appears, it is used as an abbreviation for "segment of a peripheral pipe". The only reason for these abbreviations is to simplify the writing of the document. In another embodiment of the invention, it is contemplated that at least a first sealed chamber is inside a tank or housing. The outer space to said first chamber and interior to the tank constitutes a second sealed chamber, whose subchambers communicate through the spacing between the periphery 10 of the subchambers of the first chamber and the inner wall of the tank. If the vat and the subchambers of the first chamber have a cylindrical shape, said spacings have an annular shape. In addition, these spacings have the property of being able to accommodate means, such as a rotating shaft or frame, capable of providing movement to the removers present in the second chamber. 15 In a heat exchanger for two fluids, we have two watertight chambers and we have to connect to each other the sub-chambers belonging to the first waterproof chamber, and the same with the sub-chambers of the second waterproof chamber. For this, the two preferred connection options are: the first chamber with central pipes and the second chamber with peripheral pipes; and the first chamber with central pipes and the second chamber with the aforementioned spacings. 25 In the second option, the first chamber is inside said tank or housing. However, the possibilities of: peripheral pipes in both cases are also contemplated; and the first chamber with peripheral pipes and the second chamber with the aforementioned spacings.

To continue with the description of the remaining elements and features of the invention, we will refer hereinafter, for reasons of clarity, to the embodiments thereof where two fluids are treated and the thermal plates have a circular shape and are concentric. Likewise, we will refer to the preferred connections, of the type, more peripheral central pipes and central pipes plus annular space, as set out above. These references will therefore have an illustrative and non-limiting nature, the adaptations of the elements mentioned for other geometries and number of fluids being obvious to the person skilled in the art. In order to help a better understanding of the nomenclature used in this document, the following four paragraphs mention the most important terms used, and how they relate to each other. - In the first chamber, the so-called first fluid circulates, and contains in its interior type I removers and the so-called first axis. Their subchambers and annular bodies are both classified as type I. In addition, the so-called central pipes, always existing, communicate to subchambers belonging to the first chamber, and never to the subchambers of the second chamber. - In the second chamber, the so-called second fluid circulates, and contains in its interior type II removers and the so-called second axis. Its subchambers and annular bodies 20 are both classified as type II. The second chamber includes two exclusive possibilities: either the presence of peripheral pipes, or the presence of a tank or housing. It is contemplated that the peripheral pipes are divided into two different types of segments, called type I and II. 25 - There are two types of blades, called I and II. Both types of removers can have blades of any type. For example, a type I remover may have type I and type II blades, and the same for a type II remover.

 - Both types of removers, can exercise any of the three physical phenomena 30, already described, of film agitation, film agitation with scratching and removal away from the surface. But it is not contemplated that both types simultaneously use the phenomenon of removal away from the surface, as already explained. That is to say,

if the type I remover, for example, applies a remote removal from the surface, the type II remover can only apply film agitation or scratching film agitation. As additional clarification, in some occasions, reference will be made to an element that has several constructive possibilities or types, but without mentioning the exact type. 5 This is in favor of a clearer wording, to avoid repetitions or because such specification does not apply or is not relevant in the explanation in question, as it may be if we speak in more general or abstract terms. For example, mention a blade, but without specifying whether it is of type I or II. The plurality of heat exchange plates, in a preferred embodiment, are circular and all aligned and perpendicular to the same axis. When treating two fluids we will have a first chamber, where a first fluid circulates, and a second chamber, where a second fluid circulates. Each camera is formed with several sub-cameras in communication. We define subchambers of type I as those 15 belonging to the first chamber, and subchambers of type II those belonging to the second chamber. Type I and II subchambers are arranged alternately, which means that between each of type I, one of type II is interposed, and vice versa.

In one embodiment, to close the volume contained in the first chamber, a body is located which we will call annular, since it has a ring shape with a circular crown section, between each two adjacent thermal plates that enclose a type I subchamber. annular body is called type I, because it encloses the first chamber, it is placed between both plates and joins them along its perimeters, by means of joints that guarantee a seal. As a result of this connection, a hollow cylindrical body 25 is obtained internally, where the bases thereof are two plates, thus defined by analogy with the base surfaces of a cylinder. Each of the cylindrical bodies thus formed encloses a subchamber of type I and must be in communication with the anterior and next cylindrical bodies of the same type, to form a single volume between all of them, said first chamber. For the communication between the various cylindrical bodies, 30 the realization of cylindrical perforations is contemplated in each of the plates, which communicate with the perforation of the previous or next plate, as appropriate, through a pipe segment. In a preferred embodiment, the perforations are located in the

center each plate and join by means of straight central segments. If the perforations and their connecting segments are arranged parallel and aligned with their centers contained in the same straight line, they can all be crossed by a first mechanical axis. This axis carries type I removers, which are the means that exert the effect of film agitation, film agitation with scratching or removal away from the surface, depending on the application. The heat exchanger comprises these means acting on at least one plate or sub chamber. The central zone of all these type I removers is crossed by the first axis, to which they are preferably fixed in a solidary manner, so that when it is rotated, said means also rotate and exert any of the three mentioned effects. In a preferred embodiment, the removers of type I are fastened to the first shaft in a removable manner, by means of mechanisms such as cotters, wedges, etc. The possibility of fastening to the shaft with freedom of movement in the axial direction is also contemplated. An example would be a remover with a hexagonal perforation in its central area, which is crossed by a section of the first axis that also has a hexagonal section, leaving a tolerance between axis and perforation that allows a transmission of the rotation movement at the same time as an axial displacement of the discoidal body along said first axis. A discoidal body is defined as one in the form of a solid cylinder with a height much lower than the radius; From this basic structure, modifications are contemplated that include perforations, striated surface instead of smooth or perimeter of the non-circular bases. twenty

We have defined the first chamber as the volume that encloses in its interior a set of surfaces fixed and sealed together consisting of plates, annular bodies and joining segments. The second chamber can be defined on the basis of the first, as the volume which, being inside the heat exchanger, is located towards the outside of said set of fixed and sealed surfaces. To delimit the second chamber and turn it into a closed space through which the second fluid can circulate, two possibilities are contemplated: introducing the set of surfaces that enclose the first chamber within the aforementioned tank or housing, which would be the outer limit of the heat exchanger, or place a second plurality of annular bodies, 30 named type II. The latter are interposed between each two adjacent plates that enclose a subchamber of type II. The annular bodies of type II have the same shape as those of type I, in this embodiment with circular crown section, and join the

perimeters of the plates between them. In this way they close, seal and delimit the volume corresponding to the second chamber. Similarly to the first chamber, the assembly formed by two adjacent plates and the annular body of type II that is fixed between them constitutes a hollow cylindrical body, and the volume it houses is a subchamber of type II. These are connected to each other by any of the 5 mechanisms discussed above. In the heat exchanger, the subchambers of type I and II are arranged alternately and approximately concentric. In the second chamber, composed of a set of subchambers of type II, means, type II removers, which allow film agitation, film agitation with scratching or removal away from the surface, depending on the application, are arranged. These means will be present in at least one of the plates or subchambers of type II. Like the type I removers of the first chamber, they develop a rotary movement, but on the contrary the point of application of the force that drives them is further away from the central area, being able to be peripheral. This is because they have the particularity of having a perforation in their central area, to be crossed by the central segment present in said subchamber of type II. For this purpose the perforation has a diameter greater than the outer diameter of the central segment, with which it is preferably concentric. Through the annular space that they conform, the fluid that flows through said subchamber of type II passes. The type I and II removers, in a preferred embodiment, comprise a discoidal body on whose base surfaces the blades are fixed perpendicular, so that they rotate when the discoidal body is rotated. The blades can be straight or curved, and can approach the thermal plates as much as desired, but never make physical contact. The possibility of fixing them with means that do have the capacity to exert contact and scratching on the plates, such as blades or brushes, may be metallic, plastic or any other suitable material. The blades described here, together with the scratch attachment if necessary, generate the desired effect of film stirring, film stirring with scratching or removal away from the surface. The possibility of absence of the discoidal body is also contemplated, in which case the blades are held directly on the shaft, although it is not a preferred option.

 As for the fastening means of both types of removers, a suitable design of the first axis makes it sufficient to support those of type I. Type II removers, however, do not rest on the means that provide them with movement. , which are located in an area outside its perimeter. To hold them, the possibility of placing rotating rollers in the lower area of the subchamber in question, on which the type II remover weights, while facilitating rotation movement, is contemplated. As an alternative to the rollers, the central segment that passes through the sub chamber can be designed with a suitable resistance to support the weight and rotational movement around that of the type II remover. For this, fixing rods are fixed perpendicular to its outer surface, for example by welding one of its two ends. As an example, four rods can be contemplated, each according to the direction of a radius of the segment, and each separated by 90 ° from the adjacent ones. An annular piece with a circular crown section that acts as a sliding track, for example by welding, is fixed to the free ends of the rods. The outer surface 15 of said piece has a diameter slightly smaller than that of the perforation, in this case cylindrical, made in the type II remover. In a practical case, the difference can be 1 mm. In this way the remover can be placed so that the sliding track is inside its perforation. The weight of the remover is thus supported by the track, which in turn transmits it through the rods to the central segment 20. At the same time, the first slides over the second, promoting the movement of rotation of the remover. Since the difference in diameters is small, possible vibrations during movement are avoided.

The assembly formed by the sliding track and the perforation is equivalent to a bearing 25 with sliding contact. The separation between the two surfaces in contact, the result of the difference in diameters, is filled with part of the treated fluid, which thus forms an interposed film. The effect achieved is a reduction in the friction coefficient, which reduces the wear of the pieces and facilitates rotation. Depending on the viscosity of the fluid, the separation to be left between both surfaces 30 will be greater or lesser. A significant reduction in friction is achieved for all liquid fluids, including pure water, although the higher the viscosity the better lubrication. In the case of gases, it is contemplated that the surfaces in contact are of some material

self-lubricating, such as that used in the usual sliding contact bearings, for example of polymeric nature. As described above, the center of each of the subchambers of type II is crossed by a central segment that connects two subchambers of type I. The interior space 5 to said segment therefore belongs to the first chamber, while its space outside the second chamber. With this restriction, subchambers of type II cannot be connected via central segments. To solve it, in one embodiment of the invention peripheral segments are used, which communicate the peripheries of two consecutive Type II sub-chambers. The peripheral segments are preferably outside the annular bodies, and connect said pair of subchambers by bridge or bypass to the subchamber of type I that is in the middle of both. This provision guarantees the necessary tightness so that the two fluids do not come into contact. It should be noted that it is contemplated that peripheral segments can be placed in any number and position. Thus, between two consecutive subchambers, contact can be established not only by means of a peripheral segment but by more than one, in different locations. Similarly, the placement of the segments can change between different pairs of consecutive sub-cameras. For example, suppose a heat exchanger with three consecutive Type II subchambers, called A, B and C. Between A and B there may be a peripheral segment at the highest point of the annular bodies 20, and between the consecutive subchambers B and C the peripheral segment can be located diametrically opposite with respect to the previous one, that is to say at the lowest point. With this type of arrangement, the fluid is zigzagged along the exchanger and an adequate speed thereof is guaranteed by all plates. A case of particular interest is the embodiment of the invention in which each pair of consecutive Type II subchambers 25 communicate through a single peripheral segment, and when assembling the exchanger all peripheral segments are concentric and aligned along The same axis. For example, all of them at the highest point of the subchambers. This configuration facilitates that the peripheral segments can be crossed by a second axis. 30

As mentioned, the driving force that rotates type II removers acts on a point away from its center. In a particular case, it can be a point

peripheral, for example on gear teeth located on the periphery of the discoidal body. In another contemplated possibility, the remover may comprise a first discoidal body on which a second discoidal body of smaller diameter is welded, concentric with it, on which gear teeth are arranged which are driven from an axis through a chain of transmission. In the latter case, the driving force 5 remains away from the center of the remover although it is closer than in the first case. It should be noted that in this document, where gear teeth are mentioned for the operation of removers, the possibility of their replacement by pulley belts, belts or other equivalent mechanism is also contemplated. 10 In the case where the second chamber is delimited by the tank or housing, the option of joining all type II removers together is contemplated. For this, an area of the periphery of its discoid bodies, or of the blades, if they lack them, is fixed to a bar perpendicular to them and that runs the length of the exchanger. This fixation can be for example by welding or screwing, and the number of bars and their relative position is chosen depending on the application. The set of arranged bars constitutes a framework that surrounds the removers. In order for the removers attached to the bars to rotate 360º, they must avoid collision with the rest of the parts present in the exchanger, mainly the structure of hollow cylindrical bodies that delimit the first chamber. This is achieved by providing type II removers of a diameter smaller than the inside diameter of the vessel or housing, and larger than the outside diameter of said hollow cylindrical bodies. Thus they can complete a cyclic rotation movement without obstacles. The bars to which they are fixed are connected to drive means, such as an electric motor, pneumatic motor, etc. which rotate them around the imaginary axis that crosses the center of type II removers. 25

In the embodiment in which the second chamber delimits its volume by means of a set of annular bodies of type II, it has peripheral segments and removers with a discoidal body, the preferred mode of transmission of movement to the removers is by means of gears. A first set of gear teeth can be located at the perimeter of their discoid bodies, engaging with the gear teeth of smaller diameter wheels that are fixed to the second rotating shaft. It passes through the interior of at least one peripheral segment, with which it is concentric. Axis and segment

thus they form an annular space, through which the fluid circulates. The axle sprockets are housed in a section of the peripheral segments that has an opening that allows the physical contact of the cogwheel with the remover with which it meshes. This same opening also serves to allow the fluid to leave the subchamber towards the pipe segment, move through it and flow into the next subchamber through another opening like the previous one; and in this way making its route along the exchanger. Cogwheels, concentric with peripheral segments, can keep as small a separation as each application needs. In an exemplary embodiment, the inner diameter of the segment is 1.5 mm larger than the outer diameter of the cogwheel it houses. This clearance generates a very important loss of load in the fluid and as a result it does not pass through the wheel, which blocks its passage in the longitudinal direction of the segment, but is forced to change direction towards the opening mentioned in the previous paragraph. This allows physical contact and meshes between cogwheel and remover. With this arrangement of the sprockets, the fluid is forced to take the desired steering turns and meander in the exchanger. It is contemplated that the sprockets are fixed to their axles by means such as cotters, pins, wedges, etc. which allow the wheel to move along the axis once removed. It is also contemplated that the sprockets have a polygonal perforation in its central part, which is crossed by a section of the axle that drives it that has a section with the same polygonal shape. As an example, it can be a hexagonal perforation. There is a gap between drilling and axle that allows an axial sliding of the wheel, especially important in assembly and disassembly tasks, and at the same time allows a proper movement transmission.

Another property of the embodiment in which the second chamber is closed by annular bodies of type II, is that it allows rapid assembly and disassembly. This capacity is analogous to the rapid assembly that some of the exchangers that the skilled person 30 would identify as "plate heat exchanger" allow. For this, the plates and annular bodies do not meet all their welded contact edges but rather a plurality of them contact under pressure, with the interposition of a gasket.

tightness Once this pressure is released, the elements can separate quickly, which speeds up cleaning, inspection, repair, etc. and then reassembled. The assembly of elements thus assembled is placed between two support plates, which approach each other by means of the action of some pressure screws, compressing said assembly. Each of both support plates has a foot 5 that supports it on the ground, while the compressed elements, although it is contemplated that they have their own foot, in a preferred embodiment they are suspended at a certain distance above the ground. To ensure that all the elements remain suspended in the air once the pressure is reduced and to facilitate its horizontal displacement, support bars are available. On the periphery of a plurality of modular elements, especially in their annular bodies if they have them, a fastener element having a cylindrical perforation is fixed. In a practical case, these elements can be four, each located on a quadrant of the same circle. With the exchanger assembled, each clamping element is aligned and coaxial with the analogous elements of the anterior and / or next annular bodies, so that they can be traversed by the same straight support bar. These bars also pass through the support plates through perforations enabled for this purpose, and support the weight of all suspended components, while allowing them to slide over them. In an embodiment of the invention with four fasteners for each annular body, four aligned rows are formed that will be traversed by four support bars. Once the pressure generated by the screws between the two support plates is released, they can be separated and therefore also the components between them. The length of the support bars is such that it allows a separation between the different components (annular body, 25 removers, etc.) sufficiently comfortable for cleaning, maintenance and repair operations.

The components in the middle of both support plates are grouped into independent modules. The various elements that make up each individual module (annular body 30, thermal plate, etc.) are fixed by fixed joints such as welds. The joints between each pair of adjacent modules are preferably removable, for example consisting of the interposition of a seal and exerting a pressure. In

Depending on the application, three possibilities are contemplated when forming the modular elements, which constitute three different embodiments of the disclosed invention: -1) First option: Heat exchanger with two types of modular elements, called type I and II , arranged alternately. The modular element of type I is established with the fixed joint, for example by welding, of an annular body of type I with a thermal plate and a peripheral segment of type I. The modular element of type II is established with the fixed joint between an annular body of type II, a thermal plate, a central segment and a peripheral segment of type II. The thermal plates of both 10 types I and II have a hole in their center. In the type II element, the central segment is fixed concentrically with the thermal plate, which carries in its center a perforation of diameter approximately equal to the inner diameter of its central segment, thus allowing the circulation of the fluid along of the. At the opposite end, the segment has a flange with nut holes, which allow it to be fixed to the thermal plate of the adjacent modular element, type I. This connection is made by interposing a seal and pressing with the nuts. These cross both the flange of the central segment and the adjacent thermal plate, which is equipped with the necessary perforations in correspondence. Likewise, said adjacent plate has a central perforation of approximately equal diameter to the inner diameter of the central segment, and thus allowing the free passage of the fluid through its interior. When the modular elements are arranged alternately, between each of type II is found one of type I and vice versa. The peripheral segments communicate each pair of consecutive modular Type II elements. In this way the fluid passes from one element to the next by bridging the type I element that they have in the middle. With the exchanger assembled, aligned pairs of peripheral segments of type I and II are formed respectively, their edges being in contact under pressure, with interposition of a gasket that is tight. 30 The peripheral segments of type I are fixed to the periphery of a modular element of type I, but so that the internal volume to the segment does not communicate with the internal volume of the modular element to which it is fixed.

 Type II peripheral segments are fixed to the periphery of a type II modular element, but presenting an opening that communicates both volumes and so that the fluid can pass from the segment to the modular element therethrough, and vice versa. 5 The existence of joints in the joints between adjacent peripheral segments and also in the joints between annular bodies and adjacent thermal plates, supposes a double sealing barrier that prevents accidental mixing of the different fluids. In this document they are named as double joints, and consist of two physically separated sealing elements, but which are treated as a single joint. Between both elements there is a space open to the atmosphere, so that before any leak the fluid is vented to the outside without the risk of mixing. In this first option, both in the first and second chamber there are nuts that are bathed by the respective fluids. If for reasons of hygiene, in some 15 applications there should be no nuts, they can be replaced by a welded joint, as occurs in the realization of the exchanger that will be discussed below, which also has the advantage of facilitating assembly and disassembly of the exchanger very fast. Finally, although in the union with nuts the possibility of leaks through the joints is unlikely, due to the great pressure that can be exerted on them, in the embodiment with welded joint this possibility can be considered void for practical purposes. -2) Second option: Heat exchanger with three types of modular elements, which we will call type III, IV and V. Element III is formed by two 25 adjacent thermal plates and a central segment located between them. All these elements are fixed together, for example by welding, joining the first end of the segment to the center of one of the thermal plates, and the second end to the center of the thermal plate adjacent to the previous one. To provide greater rigidity to the assembly, connecting bars can be interposed between the two plates and perpendicular thereto, with each one of its two ends fixed to its respective plate. These bars are preferably placed welded to the periphery of the plates.

Finally, it is contemplated that one of the two thermal plates of the type III modular element has a larger diameter than the other. With this configuration, it is intended that by having said modular element concentric with a modular element of type IV, with an annular shape and of a diameter comprised between that of one and another plate, said type IV element may contain inside the plate smaller than the time that exerts pressure, with 5 interposition of a board, on the greater one, that acts as a stop. With this configuration, the modular elements of type III and IV enclose in their interior a waterproof subcamera (type II) and removable for the passage of a fluid. The modular element of type IV, already mentioned, comprises an annular body of type II 10 which has a peripheral segment of type II fixed on its exterior, which has an opening that puts them in communication. The modular element of type V houses inside it a subchamber of type I. It comprises an annular body of type I, of smaller diameter than the annular body of the modular element 15 of type IV, with which it is placed adjacent and exerts pressure, with interposition of a seal. Being two annular bodies with different diameters, to allow contact between the two, the surface of the largest diameter (type II, belonging to the modular type IV element) is extended by means of a flange along its circumference. On the outside of the annular body of the type V element, a peripheral segment of type I is fixed, which does not have an opening that communicates the spaces enclosed by the segment and the annular body. To mount the exchanger, the type III element is introduced into the type IV as described, and this unit thus assembled in detachable mode is arranged alternately with the modular type V element along the exchanger. In this way, between every two units formed by the introduction of the type III element into that of type IV, a type V unit is interposed, and vice versa.

Clamping elements are contemplated for all the aforementioned modular elements, named of type I, II, III, IV and V, comprising a hole traversible by a support bar, as already described. These keep those elements without a support foot suspended in the air and facilitate their sliding through them,

assembly and disassembly. -3) Third option: Heat exchanger with a single type of modular element, which we will call type VI, which comprises: a first thermal plate; a second thermal plate; a central segment with one of its ends immobilely connected to the center of the first thermal plate, and the opposite end immobilely connected to the center of the second thermal plate; and an annular body, of type I, immovably fixed to the first or second thermal plate. 15 Type VI modular elements are arranged in series and in the internal volume of a tank or housing, so that inside the modular elements is the first chamber and outside and inside said housing, the second chamber . In the contact areas between each two adjacent elements, gaskets of 20 are interposed, which can be double. Additionally, the joints can be reinforced with nuts or a plurality of the joints can also be dispensed with and replaced by welded joints.

In one embodiment of the invention, type I and II removers are driven by two rotating shafts, as already seen. A first axis runs through the first chamber and drives the type I removers inside. A second axis runs through the second chamber and drives the type II removers inside. In both cases, the fluid bathes the shaft walls. In turn, the axes are actuated by means external to the chamber in which they act. In one embodiment these means are motors, preferably electric, combustion or pneumatic. A single motor can be provided that drives both axes or, more conveniently, one motor for each axis. In this way, the rotation speeds of each set of removers can be controlled

in an independent way. This presents a great advantage, since the conditions of agitation required do not usually coincide. In a practical example, a very viscous fluid requires vigorous agitation to destabilize the boundary layer, while a low viscosity fluid or condensing gas requires much less agitation to achieve an equivalent result. An equalization of the rotation speeds with the 5 of the most unfavorable fluid would in any case imply an unnecessary energy cost overrun. And in certain cases, regardless of energy consumption, excessive removal can trigger a malfunction. For example, in certain applications where a fluid is boiling, a film heat transfer coefficient above certain values, due to excessive agitation, can trigger unwanted phenomena such as steam blocking and instability. To allow the output of the shafts from the chambers to the outside of the exchanger, where the motors or other drive means are located, without the fluid leaking outside, or an acceptable level of them, they are passed through a mechanical seal 15 or equivalent. Mechanical seals, gaskets, labyrinth seals and other mechanisms that perform a similar function are contemplated. In order to support the shafts and facilitate their rotation, they are passed through bearings fixed to the support plates. In a particular embodiment, they are rolling contact bearings. 20 The installation of support bases welded to the support plates is also planned, in order to support and accommodate the motors in a position aligned with the driving axes. For the connection between both elements, a flexible coupling is preferably provided. 25 In order to facilitate the assembly and disassembly of the exchanger, it is contemplated that the axle bearings are fixed to the support plates in a removable way, for example by nuts, clamps, etc.

Thermal plates may have a smooth or striated surface, as already mentioned. The section of a cutting plane perpendicular to a smooth plate, along a radial direction, indicates the characteristic shape of the surface. Keeping the plane so defined, the preferred striated shape generates a sinusoidal section, the result of

set up concentric grooves. With this conformation the area of thermal exchange is substantially increased per unit of exchanger volume, resulting in smaller equipment. In addition, the striated shape significantly increases turbulence, which decreases the tendency for deposits of particles and encrustations, and increases the coefficient of heat transmission. An added advantage is that it allows to withstand 5 greater pressure differences than a smooth plate. To further enhance this property, the use of reinforcing rings is contemplated. For the specific case of concentric circular grooves that follow a sinusoidal function, circular and concentric reinforcement rings welded to the grooves are contemplated. It is particularly interesting to weld them at those points of the thermal plates that correspond to maximums and minimums of said sinusoidal function. In this way a high-strength lattice structure is achieved, even for small thicknesses of the thermal plate. With a suitable choice of the thickness of the rings and the number of grooves, the thermal plate thus designed can have a thickness of only 2 mm and withstand pressure differences between both sides greater than 20 bar. This gives the heat exchanger object of the invention a great technical advantage, since many scraped surface or agitated film exchangers require large thicknesses on the heat exchange surfaces, sometimes greater than 6 mm. Such is the typical case of state-of-the-art agitated film equipment that is formed from a vertical cylindrical housing, with outer jacket, and on which a thin fluid film with mechanical agitation 20 descends. With a smaller thickness in the plates, in addition to the material savings, the heat transfer coefficient is increased. The blades, in those cases where they provide mechanisms of film agitation or film agitation with scratching, preferably have an inverse form to that of the 25 grooves of the thermal plate on which they act, adapting to it. This allows to keep constant the separation between both elements. The following describes the possible paths of the fluids along the chambers of the heat exchanger, for the embodiments that have removers with a discoidal body. In addition to supporting the blades, this body has the function of being a deflector that forces the fluid to take a certain trajectory, in addition to reducing the passage section and therefore increasing its speed.

 In the first chamber, the fluid can be displaced by the action of a hydraulic pump. This runs through the succession of central segments and subchambers of type I, both elements arranged alternately. The discoid bodies are fixed in their central part to the axis that moves them and their periphery keeps a wide distance with respect to the annular body 5 that houses them; This separation distance forms an annular space for a cylindrical exchanger. Wide distance means that which facilitates the passage of the fluid with a small pressure loss. As a non-limiting example, 2 - 5 cm can be considered. According to the exposed configuration, the fluid carries out the following path: it travels through a first central segment and flows into the center of a first subchamber of type I, 10 bathing one of both sides of the discoidal body. The fluid travels from the center to the periphery of said subchamber, where it crosses the aforementioned annular space and goes to the opposite side of the discoid body. He then goes to the central area of said opposite face and leaves this first subchamber of type I through a second central segment, which connects it with a second subchamber of type I. The fluid therefore moves in a face from the center to the periphery, and on the opposite side from the periphery towards the center. This process is repeated throughout the entire first chamber. If the blades are configured with the proper shape and resistance and rotate at the correct speed 20, in addition to the removal or agitation functions they also propel the fluid along the entire exchanger, acting in a manner equivalent to that of a hydraulic pump. In this way they allow dispensing with it, lowering the energy and construction cost of the exchanger. This phenomenon occurs by virtue of the centrifugal force they exert. 25

In the embodiment in which the blades are fixed on a discoidal body and not directly on the axis, we differentiate two different types, depending on the face thereof on which they are fixed. On one of the faces, the fluid travels from the center to the periphery; Type I blades are placed on it. On the opposite side, the fluid travels from the periphery to the center, and on it are blades that we call type II. With this arrangement, it can occur that both types of blades are counteracted and hinder the flow of fluid from the inlet to the outlet of the exchanger. a way to

To avoid this problem is to provide the blades of type II with a geometry and dimensions different from those of type I, which exert a lower centrifugal force. Thus the following trajectory is achieved: the fluid reaches the center of a first face of a discoidal body; Type I blades arranged there propel it by centrifugal action to the periphery. This path is described in the form of a spiral, therefore the fluid covers the entire area of said first face. Once it reaches the periphery, it borders the discoidal body and goes on to bathe the opposite face, which has type II blades. As the type I blades exert a stronger drive than the type II, the fluid is directed on said opposite face from the periphery to the center and exits through the central segment. Type II blades ensure that the path is spirally shaped, so that the fluid 10 bathes the entire face of the discoidal body. In a particular example, type II blades differ from those of type I in that they have a plurality of perforations through which the fluid circulates. In the second chamber, as in the first, the fluid can be displaced by the action of a hydraulic pump. The fluid runs through the succession of peripheral segments and subchambers of type II. If there are discoidal bodies in the removers, they act as baffles and provide the same advantages that were described for the first chamber. But unlike the previous ones, they have a central perforation that facilitates the passage of the fluid, while the periphery extends until it is very close to the surface of the annular body that contains them, greatly impeding the passage of the fluid through the separation distance they maintain. As a practical example, the difference between the diameter of the discoidal body and the inner diameter of the annular body may be of the order of 1 - 3 mm. This separation causes a very large pressure loss and that only a very small proportion of the fluid pass through it. According to the foregoing, the fluid path is described as follows: it crosses a first peripheral segment and flows into the periphery of a first subchamber of type II, bathing a first face of the discoidal body it contains. From there it moves to the center and is introduced through the said central perforation, bordering the discoidal body, so that it goes to bathe the opposite side to the previous one. Then it goes again to the periphery, to leave said first subchamber of type II through a second peripheral segment, which communicates with a second subchamber of type II.

Equivalent to that described for the first chamber, and following the same principles, for the second chamber the blades of type I and II can have different geometries, so that one type exerts a stronger drive than the other. In order to facilitate the diversion from the peripheral segments to the subchambers of type II and 5 vice versa, it is contemplated that the sprockets of the second axle adjust their diameter to the inner diameter of the peripheral segment that houses them in such a way that they impede the passage of the fluid in the longitudinal direction of said segment. In this way the fluid is forced to change direction and wind along the heat exchanger. 10

The different fluids enter and leave the exchanger through respective inlets and outlets. In a particular embodiment of the invention, the input is made by the first support plate, and the output by the second, or vice versa. This arrangement may have disadvantages during disassembly, since before moving one of the support plates, it will be necessary to disassemble the connections of its inlet and / or outlet with the auxiliary connection pipes. If, on the other hand, all the mouths are in the same support plate, the opposite plate can move freely, as there are no such connections. As a solution to this problem, the possibility that all the exchanger's inputs and outputs are on the same support plate is contemplated, which is achieved by segmented inlet and return pipes. The inlet leads to the fluid through the outside of the exchanger from one end to the opposite, and from there they enter and pass through it. The return pipes lead to the fluid that has already passed through the inside of the exchanger, from the outside from one end to the opposite. In preferred mode, only one type of these pipes, of access or return, is connected to each chamber. Both are fixed to the outside of the annular bodies, 25 in a manner equivalent to that described for the peripheral segments, but without openings. Once the exchanger is assembled, the segments of each inlet and / or return pipeline are aligned and pressurized, with interposition of seals between adjacent segments. As an illustrative example, the path of a fluid through the first chamber with return pipe is described: it enters the exchanger through the inlet port of the initial support plate. It goes through the entire chamber and leaves it through the exit of the final support plate. Said outlet is connected to a return pipe that makes a turn that allows the direction of the fluid to be reversed. Once in it, go through the

succession of segments and ends at the initial support plate, which leaves through the corresponding outlet. Finally, we describe below the procedure that is carried out in the plate heat exchanger object of the present invention. 5 A first fluid is introduced into the plate heat exchanger. It is driven, taking a tour of its interior, through a first waterproof camera. In said path, the fluid is agitated by means of a set of removers, which generate a physical effect on it within the group consisting of film agitation, film agitation with scratching and removal away from the surface. It is contemplated that, additionally, the removers have the ability to propel the fluid through its sealed chamber in a manner equivalent to that of a hydraulic pump. A second fluid is introduced into the plate heat exchanger, driven 15 through a second sealed chamber. Everything said in the previous paragraph for the first fluid is equally applicable to the second fluid. But as an exception, both fluids will never be simultaneously under the phenomenon of removal away from the surface. For example, if removers act on the second fluid that generate a removal away from the surface, the first fluid removers will generate an effect 20 of either film agitation or film agitation with scratching. DESCRIPTION OF THE DRAWINGS To complete the description that is being made, and in order to help a better understanding of the characteristics of the invention, a set of drawings is attached as an integral part thereof. illustrative and non-limiting nature.

The invention disclosed in this patent application comprises a large number of 30 possible embodiments, but in order to illustrate it we limit ourselves in the figures to four main ones. All of them have in common, among other properties, that the heat exchanger treats two fluids and the thermal plates have a circular shape.

These four embodiments bring together the following figures:

- Figures 1-5 and 7-11 represent an embodiment of the exchanger in which modular elements of type I and II are present, subchambers of type I are connected by central segments and subchambers of type II are connected by peripheral segments , all of them located at the highest point of the modular elements.

- Figure 6 represents an embodiment that differs from the previous one in that the peripheral segments are located at the highest point and also at the lowest of 10 modular elements.

- Figures 12-16 represent an embodiment in which the heat exchanger has modular elements of type III, IV and V.

 fifteen

- Figures 17-20 represent an embodiment of the heat exchanger in which it has a modular type VI element and type II removers fixed to a shell that surrounds them.

 The content of each individual figure is described below: Figure 1 shows a perspective view of the heat exchanger. It is expanded in such a way that a plurality of its internal components can be seen. Figure 2 shows a sectioned perspective view of the heat exchanger, once assembled. Figure 3 shows a longitudinal section of the exchanger. The movement of the two fluids is illustrated by arrows. Figure 4 shows a cross-section of the heat exchanger, through a cutting plane indicated in Figure 3. Arrows are shown illustrating the path of the fluid running through the subchamber shown.

Figure 5 is a detail view of an area of Figure 3, where the pressure junction of the peripheral segments of type I and II is seen. Figure 6 represents a longitudinal section of the exchanger, in an embodiment of the invention in which the flow of the fluid along the second chamber is different from that of the previous figures. Arrows are illustrated that illustrate the trajectories of the two fluids that run through the exchanger. Figure 7 shows a sectioned perspective view of a type II modular element assembled under pressure with a type I modular element. 10 Figure 8 shows a perspective view of a type II modular element. Figure 9 represents a perspective view of a modular type I element, with the gaskets and nuts shown in an exploded view. Figure 10 represents a perspective view of a type I remover. Figure 11 represents a perspective view of a type II remover. 20 Figure 12 shows a perspective view of a modular type III element. Figure 13 represents a perspective view of a modular type IV element. Figure 14 represents a perspective view of a modular V-type element. 25 Figure 15 shows a sectioned perspective view of an assembly comprising six assembled, pressure modules with interposition of gaskets. Two modular elements of type III are seen, two of type IV and two of type V. 30 Figure 16 shows an exploded perspective view of an assembly comprising three modular elements, of type III, IV and V, respectively.

Figure 17 shows a perspective view of two type II removers attached to an outer frame. Figure 18 depicts a sectioned and exploded perspective view of a modular type VI element, together with two closure elements. 5 Figure 19 shows a partially sectioned perspective view of the assembled heat exchanger, comprising the components of Figures 17 and 18. Figure 20 represents a longitudinal section of the heat exchanger of Figure 10 19. Arrows illustrating are shown the trajectories of the two fluids. Finally, it should be noted that to indicate the different components of each of the figures, straight lines and arrows are used. The arrows indicate that following the direction shown is a component considered as a set of subcomponents. 15 Straight lines indicate that at the point where they end, a component considered without the presence of subcomponents is located. For example, to indicate a camera, which we consider composed of a set of several connected subchambers, we use an arrow. On the contrary, to indicate a subcamera we use a straight line. Similarly, to indicate an inlet pipe, which we treat as formed by a set of pipe segments, we use an arrow, while to indicate one of its segments, which we consider without subcomponents, we use a straight line. PREFERRED EMBODIMENT OF THE INVENTION 25 Preferred embodiments of the invention are described below. This section is organized by exposing the descriptions of each figure one by one, starting with the number 1 and ending with the last, number 20. It should be noted that sometimes we make reference in this text, in parentheses, to some component that is not indicated in the figure that is being described. This is so for various reasons, such as clarity in the drawing or that the component in question is not visible in the figure. In any case, these elements are always indicated in any of the remaining figures.

 Figure 1 shows a perspective view of the heat exchanger (1), for two fluids and in an embodiment where the subchambers of type I (2) communicate via central segments (3) (not seen in this figure) and those of type II (4) by peripheral segments (5a, 5b), and presenting modular elements of type I (6) and II (7). 5 Both types of subchambers (2, 4) are not indicated in this figure. The exchanger (1) shown is expanded, to allow access to its interior and carry out inspection, repair or cleaning tasks. Each modular element (6, 7) and two support plates (8a, 8b) have several fastening elements (9), crossed by support bars (10). Said bars (10) support the modular elements (6, 7) and allow their horizontal sliding. The weight they endure transmit it to the support plates (8a, 8b), which have a support foot on the ground. For the approximation of the support plates (8a, 8b), there is a set of pressure screws 15 (12). These are provided with the necessary tightening so that the elements located between both support plates (8a, 8b) receive adequate compression. The seals (13a, 13b) that interpose between each two adjacent modular elements (6, 7) are appreciated. 20 The inlet of the first fluid (31a) and the outlet of the second fluid (32b) (both not visible in this figure), are located in the first support plate (8a), and the outlet of the first fluid (32a) and the inlet of the second fluid (31b) are in the second support plate (8b). An inlet pipe (15) is connected to the inlet of the second fluid (31b), and a return pipe (14) is connected to the outlet of the first fluid (32a). This configuration facilitates rapid assembly and disassembly, as the final support plate (8b) has no connections with auxiliary installations. The return and inlet pipes (14, 15) are fixed on the outside of the modular elements (6, 7) and on both support plates (8a, 8b). Said pipes (14, 15) maintain a tight separation between their interior space and the interior space to the modular elements (6, 7), 30 except at those ends thereof (15b, 14a) (not indicated in this figure) that they communicate with the inside of the exchanger (1).

The first axis (16) and the second axis (17) are observed. Support plates (8a, 8b) are fastened on each track through rolling contact bearings (18), detachably fixed to the plates (8a, 8b). Both axes (16, 17) are driven independently by electric motors (19), which are supported by the initial support plate (8a) by means of bases (20). 5 Both pipes (14, 15) are divided into a set of conveniently aligned pipe segments (21). A sealing gasket (22) is interposed between every two adjacent segments (21). The segments (21) that are fixed to the end support plate (8b) make a rotation that allows the direction of the fluid to be reversed. 10 Figure 2 shows a sectioned perspective view of the heat exchanger (1), once assembled and with the screws (12) exerting pressure on the support plates (8a, 8b). The first axis (16) is observed, crossing a total of three central segments (3), and the second axis (17), crossing a total of six aligned peripheral segments 15. These are of two distinct classes, called peripheral segments of type I (5a) and II (5b), as described in the previous figure. Both shafts (16, 17) are fastened to the support plates (8a, 8b) by rolling contact bearings (18) and exit to the outside of the exchanger (1) through mechanical seals (23). The motors (19) that give them movement and the bases (20) on which they rest are observed. On the first axis 20 (16) there are three type I removers (24). On the second axle (17) three cogwheels (25) are placed, each driving a type II remover (26). There are a total of five heat exchange plates (27), on which the removers (24, 26) act. Its surface is striated with concentric circumferential grooves. 25 Figure 3 shows a longitudinal section of the exchanger (1). The removers (24, 26) have a discoidal body (28) but the blades have been omitted, in order to improve the clarity of the drawing. The exchanger (1) has an inlet pipe (15) and a return pipe (14), but presenting the particularity of not being connected to the interior of the exchanger, for reasons of simplicity in this drawing.

A first chamber (29) is observed, crossed by the first axis (16). This is composed of three subchambers of type I (2), where each one is connected to the adjacent one through a central segment (3). A second chamber (30) is covered by the second axis (17), and is composed of three subchambers of type II (4). Each subchamber of type II (4) communicates with the adjacent one via a peripheral segment (5a, 5b) 5 The paths of the two fluids of this embodiment are described below. For this, their movements are represented by sinuous arrows. If the return line (14) is kept disconnected, the fluid makes the following path in the first chamber (29): it enters through the inlet (31a) of the first chamber (29) and moves, 10 through a first central segment (3), to the first subchamber of type I (2), where it bathes one of both sides of the discoidal body (28) of the remover (24) located there. Here it makes a spiral path that moves it from the center to the periphery of said discoidal body (28), where it borders it and goes to bathe the opposite face. It performs a new spiral displacement that moves it to the center of the discoidal body 15 (28). He then leaves the first sub-chamber through a second central segment (3) and passes to the second sub-chamber. The process is repeated until the fluid leaves the exchanger (1) through the outlet (32a). In the return pipe (14) we distinguish an inlet end (14a) and an outlet end (14b). If the outlet of the first fluid (32a) is connected to the inlet end (14a) of the return pipe (14), the fluid when exiting the exchanger (1) reverses its direction, it travels along the entire the return pipe (14) and ends at its outlet end (14b), which in this case would become the new fluid outlet. The advantage of this connection is that the auxiliary pipes that are connected to the exchanger (1) both for the inlet of the fluid to be treated and for the outlet of the fluid already treated (not shown herein), are both on the same Support plate. The fluid path inside the return line (14) is represented by two arrows. 30

If the inlet pipe (15) is kept disconnected, the second fluid makes the following path in the second chamber (30), for a counter-current arrangement: it enters through the inlet mouth (31b) of the second chamber (30) , go through a first

Type I peripheral segment (5a) and flows into a first type II peripheral segment (5b). The latter houses inside, at its midpoint, a first gear wheel (25) that blocks the passage to the fluid, so that it is forced to leave said peripheral segment of type II (5b), through an opening (33 ) (not noticeable in this figure) that communicates with a first subchamber type II (4), entering its peripheral area. 5 The said first gear wheel (25) blocks the passage of fluid here through one of its faces, which we call the left face. Once in the peripheral zone of the subchamber of type II (4), the fluid travels in a spiral to the center of the subchamber, where it finds the central perforation (26a) of the type II remover (26), which it crosses. In doing so it borders the remover (26), so that it passes to bathe its opposite face. Then, it spirals from the center to the periphery of said first subchamber of type II (4), which leaves through the opening (33) (not noticeable in this figure) that communicates with the first peripheral segment of Type II (5b) containing the first gearwheel (25). In this path the fluid bathes the right face of said gearwheel (25). It leaves the first peripheral segment of type II (5b) and enters a second peripheral segment of type I (5a), which it crosses, leading to a second peripheral segment of type II (5b). It is also locked by the left face of a second gearwheel (25). The process is repeated until the fluid leaves the second chamber (30) through its outlet (32b). 20 In the inlet pipe (15) we distinguish an inlet end (15a) and an outlet end (15b). To connect it to the second chamber (30), we connect the inlet of the second fluid (31b) with the outlet end (15b) of the inlet pipe (15). In this way, the inlet end (15a) becomes the new inlet of the second fluid. Through the inlet end (15a) the fluid enters, runs the entire length of the inlet pipe (15), reverses its direction in the connection with inlet port (31b), runs through the entire second chamber (30) and leaves the exchanger (1) through the outlet (32b) of the second chamber (30). The fluid path inside the inlet pipe (15) is represented by two arrows. 30

A cross section of the heat exchanger (1) is shown in Figure 4, through the cutting plane named A-A in Figure 3. This plane cuts to a modular type II element (7). For reasons of clarity some components are omitted from the drawing, such as

the union nuts (43) between adjacent modular elements and the perforations they cross, as they do not belong to the essence transmitted in this figure, and all of them are represented in other figures. The final support plate (8b), the pressure screws (12), a total of four fasteners (9) and four support bars (10) are distinguished. Likewise, the inlet pipe (15) and the return pipe (14), 5 are shown, and in broken lines the outlet of the first chamber (32a) and the inlet of the second chamber (31b). The modular element of type II (7) houses inside a remover of type II (26), of which a discoidal body (28), six blades of type I (34a), a central perforation (26a) and a periphery with gear teeth (35). They engage with the gearwheel (25) that drives the second axle (17). This wheel is located in the interior of a peripheral segment of type II (5b), which has an opening (33) that communicates with the subchamber of type II (4) that has underneath and allows the mentioned gear between wheel ( 25) and remover (26). The fluid spirals on both sides of the remover (26). A possible path 15 on the visible face is shown by arrows with thick, continuous and sinuous lines. On the non-visible face, a possible path is shown by thin, dashed and sinuous arrows. As you can see, in one case the spiral moves the fluid away from the center to the periphery, and in the opposite case vice versa, it moves it away from the periphery to the center. This opposition in the trajectories is achieved thanks to the differences in the types of 20 blades (34a, 34b). The path on the visible face is described as follows: the fluid borders the type II remover (26) through its central perforation (26a), going to bathe the face thereof visible in the drawing, which presents type I blades (34a). These have a characteristic curved shape, which causes that when they move exert a centrifugal force on the fluid that makes it spiral from the center to the periphery. Once in it, it leaves the subchamber and enters the peripheral segment of type II (5b) located above. For this, it crosses the corresponding opening (33). Once in the segment, it follows a curved path that minimizes the loss of load, thanks to the arrangement of a deflector wall (36). The fluid leaves this segment and enters the adjacent type I peripheral segment (5a), not shown in this figure.

In the center of the subchamber (4) a central segment (3) is located. Its interior belongs to the first chamber (29), where the first fluid circulates, and is crossed by the first axis (16), of which a hexagonal section is observed in the drawing. Outside the central segment (3) is located the second chamber (30), where the second fluid circulates. Four rods (37) are welded on its outer surface and perpendicularly thereto, each following a radial direction. On its second ends, a sliding track (38) is welded, on which the weight of the type II remover (26) rests. Between the track (38) and the central perforation of the remover (26a) a film of liquid is formed that reduces friction, facilitating the rotation of the remover (26). As an additional measure of securing the remover (26), two rotating rollers (39) are arranged, in 10 the lower zone of the modular element (7) and on which the remover (26) rolls. In Figure 5 we have a detail of an area of Figure 3, where the pressure junction of the peripheral segments of type I (5a) and II (5b) can be seen. For this, two different types of sealing joints are interposed, single (13a) and double (13b). According to the orientation of the drawing, a simple seal (13a) is interposed to the right of the peripheral segments of type I (5a), while to its left the joint is double (13b). This is so because on the right side the welded joints between the pipe segment and the thermal plate (27) make the mixing of the two fluids impossible, so that a joint that prevents the outflow of the fluid to the outside of the exchanger (1) is sufficient . On the left side, the pipe segment does not have welds with the thermal plate (27) to which it joins, so there is a risk of mixing between the two fluids. When using a double joint (13b), if there is a leakage of one of the two fluids, it is directed to a space that is vented (40) into the atmosphere, avoiding the risk of mixing. 25 The cogwheel (25) shown is placed on a section of the second axle (17) that has a hexagonal section, like the central perforation of the wheel (25). This facilitates the horizontal displacement of the wheel (25) in assembly and disassembly work. It can be seen that the diameter of the peripheral segments of type I (5a) is smaller than that of those of type II (5b). This was chosen for hydrodynamic reasons, 30 but they could both have the same diameter and allow the extraction of the second axle (17) with all its gear wheels (25) and with the exchanger (1) without disassembly.

In order to direct the flow of the fluid, a first deflector wall (36) is fixed on the right side of the peripheral segments of type I (5a). Inside the peripheral segments of type II (5b), a second deflector wall (36) is fixed for the same purpose. In this embodiment, the peripheral segments of type II (5b) also carry a welded disk (41) in its central area, to hinder the passage of fluid along the pipe in a manner equivalent to that of the cogwheel itself (25 ). The reinforcement rings (51), which have a circular shape, are distributed concentrically and are welded to the thermal plates (27), on the 10 highest and sunken areas of their grooves, which are also shown in Figure 5 They are circumferential and concentric. A longitudinal section of the exchanger (1) is shown in Figure 6, in an embodiment of the invention in which the flow of the fluid along the second chamber 15 (30) is different from that described above. The possible paths of both fluids are represented by sinuous arrows inside the exchanger. The peripheral segments (5a, 5b) are not all aligned on the same axis, whereby the paths change. There are peripheral segments of type I (5a) in the highest zone of the exchanger (1) and also in the lowest zone, diametrically opposite to the previous one. Given the arrangement of this embodiment, although there are three peripheral segments of type II (5b), only two of type I (5a) are necessary. The fluid inlet in the second chamber (31b) is in the lower zone, and the outlet (32b) remains in the usual location. 25 Figure 7 shows a sectioned perspective view of a type II modular element (7) pressure assembled with a type I modular element (6). Between them there is a simple seal (13a). According to the orientation shown, double sealing joints (13b) are located to the left of the modular type II element (7) and to the right of the modular type I element (6). The vented space 30 (40) is observed in the atmosphere.

Type II peripheral segment (5b) has an opening (33) (not indicated in this figure) that facilitates the passage of fluid to the subchamber underneath, which is type II (4), while allowing the engagement between the sprocket (25) and the type II remover (26). The peripheral segment of type I (5a) does not have said opening (33) and the fluid passes through it without coming into contact with the subchamber located below, which is of type I (2). 5 The discoidal bodies (28), type I blades (34a) and type II blades (34b) are distinguished. The latter have perforations (42) pierced by the fluid. The type I remover (24) has a central hexagonal bore (24a), in which a section of the first axis (16) fits with a hexagonal section. In this way the shaft (16) transmits the rotary movement to the remover (24) but in turn the latter can be moved along the shaft (16) with ease. The sliding track (38) that supports the type II remover (26) and the rods (37) that fix it on the corresponding central segment (3) are also appreciated. 15 For the union of both modular elements (6, 7), in this embodiment nuts (43) are used. On one end of the central segment (3) shown a union flange (44) is welded, with perforations for the passage of the nuts (43). Between the flange (44) and the thermal plate (27) of the adjacent modular element a sealing gasket (46) is interposed and the nuts (43) exert pressure. twenty

In figure 8 we have a perspective view of a modular type II element (7). The gaskets (13a, 13b) and nuts (43) are shown in an exploded view. On the side on which the thermal plate (27) is located, a double sealing gasket (13b) is placed, while on the opposite side it is simple (13a). The opening (33) of the peripheral segment 25 of type II (5b) which communicates it with the interior of the annular body, which is of type II (47b), is appreciated. On the central segment (3) the clamping rods (37) to which the sliding track (38) is fixed are seen. At one of its ends, the central segment (3) has a flange (44) with perforations for the nuts (43). A sealing gasket (46) is placed on it when assembling the exchanger (1). The rotating rollers (39) are also appreciated, on the lower part of the annular body (47b). Each roller (39) is housed in an individual housing (48), outside the annular body (47b). For

allow the remover (26) to rest and roll on them, a perforation is made, square in this case, on the wall of the annular body (47b). The thermal plate (27) is striated, presenting concentric circumferential grooves. In a radial direction, said grooves follow a sinusoidal function, and at points that correspond to maximum and minimum of said function, circular reinforcement rings (51) are welded, all of which are concentric. In figure 9 we have a perspective view of a modular element of type I (6), with the joints (13a, 13b) and nuts (43) shown in an exploded view. On the side on which the thermal plate (27) is located, a single seal (13a) is placed, while on the opposite side the joint is double (13b). The circular joints (22) that are placed on both sides of the segments (21) of inlet (15) and return pipes (14), which are welded on the annular body, in this case type I (47a) ). The thermal plate (27) is equivalent to that of the modular type II element (7), with concentric circumferential grooves 15 and presence of reinforcing rings (51). In its central area, however, it has a circular crown-shaped region (52), with a smooth surface and nut holes (43). This region is the one that joins under pressure with the connecting flange (44) of the central segment (3) of the modular type II element (7) located adjacently. The peripheral segment of type I (5a) is also observed. 20 Figure 10 shows a perspective view of a type I remover (24), with a discoidal body (28), type I blades (34a) and type II blades (34b). The blades have a geometry with an inverse shape to that of the plate (27) on which they act (not shown in this figure), which has concentric circumferential grooves. In this way the separation between both elements is kept constant. It is appreciated that in the center of the remover (24) there is a hexagonal bore (24a), crossed by a section of the first axis (16) with corresponding hexagonal section.

Figure 11 shows a perspective view of a type II remover (26). 30 It has a discoidal body (28) and blades of type I (34a) and II (34b) with the same considerations as for the type I remover (24). The center of the discoidal body (28)

It has a perforation (26a), suitable for being crossed by a central segment (3) (not shown in this figure) and on its periphery are gear teeth (35). A perspective view of a modular type III element (53) is shown in Figure 12. It has a first thermal plate (53a) and a second thermal plate (53b), both concentric, where the second (53b) has a smaller diameter than the first (53a). The space between both plates (53a, 53b) constitutes a subchamber of type II (4), belonging to the second chamber (30) of the exchanger (1), where the second fluid circulates. In this embodiment, the thermal plates have a smooth surface. The first plate (53a) also has a circular crown-shaped structure 10 (53c), on which the peripheral segment (5b) of a modular type IV element is pressed. Both plates (53a, 53b) are connected and solidarity with each other by means of a central segment (3) that is welded to their centers, which have a circular perforation (53d) concentric with said segment (3), so that the entry and exit of a fluid is allowed along the segment (3). On the central segment (3), a sliding track (38) with a cylindrical outer surface, in a manner equivalent to that described in the previous figures, is fixed by means of clamping rods (37) (not visible in this figure). 20 To improve the fixation of one plate with respect to the other (53a, 53b), tie rods (53e) are arranged, welded to both plates (53a, 53b) on an area of its periphery. According to the spatial orientation shown, it is observed that on the right side of the first plate (53a) a simple sealing gasket (13a) is placed, and on the right side 25 of the second thermal plate (53b) a gasket of double tightness (13b).

A perspective view of a modular type IV element (54) is shown in Figure 13. It comprises an annular body of type II (47b) and a peripheral segment of type II (5b) Said annular body (47b) houses in its interior a subchamber of type II (4). The segment (5b) has an opening (33) that communicates its interior with the interior of the annular body (47b) on which it is fixed. We distinguish a first lateral (49) and a second lateral (50) of the annular body (47b). On the first side (49), the annular body (47b) has

a flange (45) on which a modular type V element (not shown in this figure) can apply pressure. On the aforementioned flange (45) and on its inner face to the annular body (47b), a double sealing gasket (13b) is placed. On the second side (50), a simple sealing gasket (13a) is placed. In type IV modular element (54) type III modular element (53) is introduced. In doing so, the second side 5 (50) of the annular body (47b) of the modular type IV element (54) presses on the first thermal plate (53a) of the modular type III element (53), and the first side (49 ) press on the second thermal plate (53b). To allow the connection of the connecting rods (53e) of the modular type III element (53), the inner face of the modular type IV element (54) has grooves (54a) for this purpose. 10 Figure 14 shows a perspective view of a modular type V element (55). It has an annular body of type I (47a) with a smaller diameter than the corresponding one for the modular element of type IV (54), and inside it houses a subchamber of type I (2). Welded to the annular body (47a), there is a peripheral segment 15 of type I (5a), which does not have any opening that communicates its interior with the interior of the annular body (47a) on which it is fixed. We distinguish a first (55a) and a second side (55b) of the modular type V element (55). Given their symmetry, both sides (55a, 55b) are indistinguishable. On each of them a double sealing gasket (13b) is placed. The first side (55a) exerts pressure on the flange (45) 20 present in the modular element of type IV (54), and on the second side (55b) the first thermal plate (53a) of the modular element of type III exerts pressure (53) and its circular crown shaped piece (53c). Figure 15 shows a sectioned perspective view of a set of six assembled modules, under pressure with interposition of gaskets (13a, 13b). Specifically, there are two modular elements of type III (53), two of type IV (54) and two of type V (55). The remaining components necessary to build the exchanger (1), such as support plates, motors, pressure screws, etc. are omitted from this view, because they are identical to those of the previous embodiments. 30

As can be seen, modular elements of type III (53) are introduced into modular elements of type IV (54). The block thus formed by both elements

Modular (53, 54), available alternately with the modular elements of type V (55). That is, between each of the blocks thus defined, a modular element of type V (55) is interposed, and vice versa. Between each two modular elements in contact, the joints (13a, 13b) that we have shown in the figures of the individual modular elements are interposed. 5 The main advantage of this embodiment is that no union nuts (43) are used between adjacent modular elements, increasing hygiene and rapid assembly and disassembly. As in the previous embodiment, the means for connecting consecutive subchambers of the same type are central (3) and peripheral (5a, 5b) segments, and the 10 removers remain equivalent, type I (24) and II (26) . Similarly the flows of both fluids along the exchanger (1) remain equivalent. It is appreciated that all peripheral segments (5a, 5b) have the same diameter, this being larger than that of the sprockets (25), driven by the second axle (17). In this way, the assembly formed by the second axle (17) and gear wheels (25) can be removed from the exchanger (1) without the need to disassemble the modular elements. This is of particular advantage in inspection and repair operations. In order that when the so defined set of axle (17) and gear wheels (25) is removed, a type II remover (26) cannot block the passage to the gear wheels (25), the result of a turn of 20 this one that causes a disengagement with the wheel (25) that is going to cross it, rails (56) are placed on the sprockets (25). These act as an extension of some of the teeth they possess and join between the adjacent sprockets (25). To remove the assembly, the wheels (25) are rotated so that the rails (56) engage with the type II remover (26). Once in this position, any rotation of the shaft (17) is avoided and 25 is removed. In this embodiment, deflector discs (57) attached to the second axis (17) are also incorporated, in order to contribute to the blockage of the longitudinal movement of the fluid at that point of the peripheral segment, in a manner similar to that produced by the cogwheel 30 itself ( 25).

The sprockets (25) actuate type II removers (26), in this embodiment with discoidal body (28) and blades type I (34a) and II (34b). The remover (26) has the central perforation (26a) necessary for the passage of a central segment (3) and the fluid through the resulting annular space between said segment (3) and the perforation (26a) that it crosses. Sliding tracks (38) are observed attached to the central segments (3) 5 by means of clamping rods (37). Type II removers (26) are located within the inner subchamber to the modular elements of type III (53) and IV (54), which is a subchamber of type II (4). Type I removers (24) are driven and supported by the first shaft (16), which crosses the interior of the central segments (3). In this embodiment, they have a discoidal body (28) and blades of type I (34a) and II (34b), but with the particularity, not limiting the scope of the invention, that both types of blades are equal in their geometry, extending in a radial direction. These removers (24) are located in the inner subchamber to the modular elements of type V (55), which is a subchamber of type I (2). 15 Figure 16 shows an exploded perspective view of a set of the three different modular elements introduced in this embodiment, called type III (53), IV (54) and V (55). They are aligned and in the positions prior to assembly by compression. Likewise, all the gaskets 20 (13a, 13b) that are involved in said assembly, already arranged in the proper place and orientation, as well as the first (16) and second axis (17) are also represented. In the second axle (17) the sprockets (25) and the rails (56) are appreciated. As can be seen, the double sealing gaskets (13b) are in one case concentric circular elements, and in other cases external circular elements. In the first case, the space to be vented (40a) to the atmosphere is that comprised in the circular crown formed by both circles, and in the second case, it is the space (40b) external to both circles. Figure 17 shows a perspective view of two type II removers (26) fixed to an outer frame (58), according to the embodiment comprising a first chamber (29) inside a tank or housing (59 ).

They have a discoidal body (28) and blades of type I (34a) and II (34b) straight, to extend according to radial directions. It is appreciated that the frame (58) comprises four bars (58a), each of them with an approximate "U" shape in this embodiment, welded to points on the periphery of the removers (26), all of which are in solidarity, so that the movement of the frame (58) transmits movement to the removers (26). The four 5 bars (58a) extend to be fixed on two sprockets (60), one at each end. Said wheels (60) have a central perforation (60a) and on them acts a driving means, such as an electric motor, not shown in this figure. Figure 18 shows a sectioned and exploded perspective view of a 10 modular element of type VI (61), together with two closure elements (62) that join at its ends, with interposition of sealing gaskets (13a) and application of pressure by means of nuts (43), in order to form a surface that houses the first chamber (29) inside. On the outside of said surface, the second chamber (30) is located, both chambers (29, 30) being hermetically separated. The two closing elements (62) shown have extensions (62a) to which both inlet (31a) and outlet (32a) mouths are connected, for the first fluid, which runs through said first chamber (29). The modular element of type VI (61) comprises an annular body of type I (47a), two 20 thermal plates (61a, 61b) (in this embodiment they are of smooth surface) and a central segment (3) interposed between both thermal plates (61a, 61b). All these components are welded. The annular body (47a) houses in its interior a subchamber of type I (2), and between the two adjacent thermal plates (61a, 61b), and outside the central segment (3) that joins them, there is a subcamera Type II (4). The interior of said segment (3) belongs to the first chamber (29). In the embodiment of the described invention, a single modular type VI element (61) is used, but the serial arrangement of as many as is necessary for each application is contemplated.

In Figure 19 we have a partially sectioned perspective view of the assembled heat exchanger (1), comprising the components of Figures 17 and 18. It has two modular elements of type VI (61) and therefore four thermal plates. The first chamber (29) is the volume inside the set

assembly of both modular elements of type VI (61) and two closing elements (62). It comprises three subchambers of type I (2), each housing a remover of type I (24). These have a discoidal body (28), blades of type I (34a) and II (34b) and are crossed in their central part by a first axis (16), which transmits the rotational movement while supporting them. Said first axis (16) crosses the 5 central segments (3) (not noticeable in this figure), and is supported by two bearings (18), which are fixed to the walls of the exchanger (1) at the points through the which shaft (16) goes outside. The assembly formed by modular elements of type VI (61) and closing elements 10 (62) assembled, is located inside a cylindrical housing (59). Said housing (59) is composed of a lateral body (59a) and two bases (59b), thus defined by analogy with the lateral body and bases of a cylinder. Each of the bases (59b) is attached to one end of the lateral body (59a) in removable form, by means of nuts (43) and with interposition of sealing gaskets (13a). The second chamber (30) is the volume that being inside the casing (59), is external to the modular elements of type VI (61) and its closing elements (62). This consists of two subchambers of type II (4). Each of them houses a type II remover (26), comprising a discoidal body (28), blades type I (34a) and II (34b). Both removers (26) are fixed to a frame (58). Each base (59b) of the housing (59) has a central opening (59c), which is crossed by an extension (62a) of the closing elements (62) and by the first axis (16). To these extensions (62a), the inlet (31a) and outlet (32a) of the first chamber (29) are connected. The inlet and outlet nozzles for the fluid flowing through the second chamber (30), consist of the annular spaces between the outer surface 25 of said extensions (62a) and the inner surface of the central openings (59c) of the housing (59). In said annular spaces, the sprockets (60) that are fixed to the frame (58) are also housed. The extensions (62a) are concentric with said wheels (60) and pass through them through their central perforation (60a). 30

Those additional elements that are necessary to complete the exchanger (1), such as engines, support bases, mechanical transmissions, etc. have been omitted from the drawing

by being outside the essence of this embodiment of the invention, and can be incorporated in a manner equivalent to those of the previous embodiments. In this embodiment, the frame (58) is supported by resting directly on the inner face of the housing (59). The presence of removable joints, by means of nuts of union (43), allows the disassembly of exchanger (1), to carry out inspection, cleaning and repair tasks. Figure 20 shows a longitudinal section of the heat exchanger (1) of Figure 19. The housing (59) and its two central openings (59c), the two modular elements 10 of type VI (61), both are shown closing elements (62) and their extensions (62a), the inlets (31a) and outlet (32a) of the first fluid, type II removers (26) fixed to a frame (58), gear wheels (60), type I removers (24) and the first shaft (16). Both types of removers (24, 26) are shown with the discoid bodies (28) but without the blades (34a, 34b), in order to increase the clarity of the drawing. In order to give support to the housing (59), a first set of support elements is available on the ground (63). To support the assembled assembly of modular elements of type VI (61) and closure elements (62), the extensions (62a) of the latter are fixed on a second set of support elements on the ground (64). The solidarity set of type II removers (26) and frame (58) rests on the inner wall of the housing 20 (59). The first fluid travels through the first chamber (29) and performs the path shown by arrows, which mostly have a sinuous stroke. The second fluid, for a countercurrent arrangement, follows the path indicated by arrows, of mostly sinuous stroke, along the second chamber (30). As can be seen, the periphery of type II removers (26) is close enough to the inner wall of the housing (59) enough to greatly limit the passage of fluid through the separation they leave, forcing it to wind by the exchanger (1). 30

An embodiment of the method associated with the plate heat exchanger object of the present invention is described below. A first fluid enters the exchanger and runs through a first chamber, from its entrance to its exit, and

Leave the exchanger. In said path the first fluid is subjected to the action of a remover near the exchange surface, located inside the first chamber. Said action includes film stirring and fluid delivery in a manner similar to that of a hydraulic pump. In turn, a second fluid enters the exchanger and travels through a second chamber, from its entrance to its exit, to then leave the exchanger. In said path, the second fluid is subjected to the action of a remover near the exchange surface, located inside the second chamber. Said action includes film stirring and fluid delivery in a manner similar to that of a hydraulic pump. 10 In addition, two applications of special interest are contemplated within the procedure. First, the first and / or second fluid comprises a gas to condense and its condensate film is removed from the heat exchange plates by means of the remover. Second, the first and / or second fluid is a gaseous mixture with a fraction that is intended to condense, but with the presence of another fraction with incondensable gases. fifteen

Claims (9)

CLAIMS 1.- HEAT EXCHANGED FILM HEAT EXCHANGER, comprising a plurality of heat exchange plates arranged in series and the following elements: a first sealed chamber (29), through which a first fluid circulates; a second sealed chamber (30), where a second fluid circulates; 10 removers, called type I (24), which describe a rotation movement and are located inside the first chamber (29); removers, called type II (26), which describe a rotation movement and are placed in the second chamber (30); 15 where at least one of both types of removers, I (24) or II (26), is a remover near the exchange surface; and characterized in that it further comprises a plurality of modular elements 20 assembled in series, several of which comprise heat exchange plates (27), and between each two adjacent plates (27) and between the initial and final plates (27) and the ends initial and final exchanger (1), respectively, a subchamber is defined; so that each chamber of the exchanger (1) is composed of a set of subchambers. 2. 2. AGITATED FILM HEAT EXCHANGER, according to the preceding claim, characterized in that the modular elements are assembled by removable joints, so that the heat exchanger (1) can be disassembled to carry out tasks comprising inspection, repair, cleaning and maintenance, and then reassembled. 3.- HEAT EXCHANGED FILM HEAT EXCHANGER, according to any of the preceding claims, characterized in that type I (24) and II removers (26) allow them to be operated independently of each other; in this way being able to move at different speeds, adapted to each fluid and process. 4.- HEAT EXCHANGED FILM HEAT EXCHANGER, according to any of the preceding claims, characterized in that the type I (24) and / or 5 II (26) removers comprise a mechanical structure that makes them suitable for fluid delivery, in a similar way to a hydraulic pump. 5.- HEAT EXCHANGED FILM HEAT EXCHANGER, according to any of the preceding claims, characterized in that the type I removers (24) 10 have a hole (24a) in its central area that is crossed by a rotating first axis (16), which gives them the rotation movement, where said shaft (16) has means for securing the heat exchanger (1) and that facilitates its rotation and means that guarantee the sealing between the shaft (16) and those parts of the exchanger ( 1) that are crossed by it to allow its exit abroad; in this way 15 limiting fluid leaks. 6. AGITATED FILM HEAT EXCHANGER according to claim 5, characterized in that the type I removers (24) comprise: a discoidal body (28), which has the central hole (24a) in which the first axis fits (16); and at least one blade, fixed on the discoidal body (28). 7. AGITATED FILM HEAT EXCHANGER, according to any of claims 5 or 6, characterized in that the orifice (24a) of the remover (24) has a polygonal shape, into which a section of the first axis (16) is introduced which It has the same polygonal shape, in cooperation with the hole (24a), allowing a clearance between the two that facilitates the longitudinal movement of the remover (24), especially of relevance in assembly and disassembly operations, while allowing a transmission of the proper movement 8.- HEAT EXCHANGED FILM HEAT EXCHANGER, according to any of the preceding claims, characterized in that the type II removers (26) are driven by a second rotating shaft (17) located in an area outside its perimeter, where said axis ( 17) it has some means of attachment to the heat exchanger (1) and that facilitate its rotation and means that guarantee the sealing between the shaft (17) and 5 those parts of the exchanger (1) that are crossed by it to allow its exit abroad; in this way limiting fluid leaks. 9- AGITATED FILM HEAT EXCHANGER, according to claim 8, characterized in that the type II removers (26) comprise: a discoidal body (28), with a central hole (26a); at least one blade, fixed on said discoidal body (28); and 15 means that allow the transmission of movement from the second axis (17), located in an external position to the perimeter of the discoidal body (28), to the type II remover (26). 10.- AGITATED FILM HEAT EXCHANGER, according to claim 9, characterized in that the means that allow the transmission of movement comprise a mechanism within the group consisting of gearing teeth (35) and pulley bands. 11.- AGITED FILM HEAT EXCHANGER, according to claim 10, characterized in that the means that allow the transmission of movement comprise gear teeth (35) located on the periphery of the discoidal body (28). 12.- HEAT EXCHANGED FILM HEAT EXCHANGER, according to any one of claims 10 or 11, characterized in that a plurality of gear wheels (25) that engage with the teeth (35) that the body is placed on the second axis (17). discoidal (28) possesses, and in this way transmitting the movement.  13.- AGITATED FILM HEAT EXCHANGER, according to claim 12, characterized in that the sprockets (25) have a central perforation in the shape of a polygon, which is crossed by a section of the second axis (17) that has the same shape polygonal, in cooperation with the hole, in this way 5 allowing a clearance between the two that facilitates the longitudinal displacement of the gearwheel (25), of special relevance in assembly and disassembly operations, while allowing a proper movement transmission . 14.- HEAT EXCHANGED FILM HEAT EXCHANGER, according to any one of claims 12 or 13, characterized in that the sprockets (25) have a diameter that approximates the inner diameter of the conduit that houses them, so that they impede the passage of the fluid along it and force it to change direction. 15.- HEAT EXCHANGED FILM HEAT EXCHANGER, according to any of the preceding claims, characterized in that every two consecutive sub-chambers (2) belonging to the first chamber (29), communicate through central segments (3), which cross the interior of the subchambers that stand between them; and where every two consecutive subchambers (4) belonging to the second chamber (30) communicate through peripheral segments (5a, 5b), which border on the outside 20 of their perimeter to the subchambers that interpose between them. 16.- AGITATED FILM HEAT EXCHANGER, according to claim 15, characterized in that the modular elements it possesses are classified into two different types and arranged alternately, called modular elements of type I (6) and II (7), respectively, where the subchambers (2) of the first chamber (29) are housed in those of type I (6), and the subchambers (4) of the second chamber (30) are housed in those of type II (7); the modular elements of type I (6) comprising an annular body (47a), a thermal plate (27) and a peripheral segment (5a); and those of type II (7) comprising an annular body (47b), a thermal plate (27), a central segment (3) and a peripheral segment (5b). 17.- AGITED FILM HEAT EXCHANGER, according to the claim 15, characterized in that the modular elements it possesses are classified into three distinct types, called modular elements of type III (53), IV (54) and V (55), the type III (53) comprising two thermal plates (27 ) contiguous and a central segment (3) that is placed between them, with each end attached to one of the plates; those of type IV (54) comprising a peripheral segment (5b) and an annular body (47b), 5 in which the modular element of type III (53) is introduced, thus forming both types III (53) and IV (54 ) a unit; and the type V (55) comprising an annular body (47a) and a peripheral segment (5a); alternately disposing the unit formed by types III (53) and IV (54) with the modular element of type V (55), so that the sub-chambers (4) belonging to the second chamber (30) are housed in the first, and the 10 sub-chambers (2) belonging to the first chamber (29) are housed in the second; achieving with this arrangement of the heat exchanger (1) a rapid assembly and disassembly and its suitability for conditions where hygiene is of great relevance. 18.- AGITATED FILM HEAT EXCHANGER, according to any of the preceding claims, characterized in that it comprises support means capable of holding suspended in the air, once the exchanger (1) has been disassembled, to those modular elements that do not have a support foot on the ground; also allowing a horizontal displacement of them, thus facilitating the tasks of assembly and disassembly for cleaning, maintenance, inspection and repair. 19.- AGITATED FILM HEAT EXCHANGER, according to claim 18, characterized in that said support means comprise at least two support plates (8a, 8b), each with a support foot on the floor, said 25 plates located on both ends of the exchanger (1) and with means for approaching each other in such a way that they compress the set of modular elements, which has been placed between them. 20.- AGITED FILM HEAT EXCHANGER, according to claim 19, characterized in that the means allowing the approximation of said support plates (8a, 8b) comprise screws (12). 21.- HEAT EXCHANGED FILM HEAT EXCHANGER, according to any of claims 1-7, characterized in that the type II removers (26) are fixed to a frame (58) that surrounds them, so that when equipped with a movement rotating, rotate with it type II removers (26). 22. 22. AGITATED FILM HEAT EXCHANGER, according to claim 21, characterized in that the type II removers (26) comprise: a discoidal body (28) with a central hole (26a); and 10 at least one blade, fixed on said discoidal body (28). 23.- HEAT EXCHANGED FILM HEAT EXCHANGER, according to any of claims 6, 9-14, or 22 characterized in that the blades have a mechanical shape, dimensions and resistance that makes them suitable for propelling the fluid in a manner similar to that of a hydraulic pump, by virtue of the centrifugal force they generate. 24.- AGITATED FILM HEAT EXCHANGER, according to claim 23, characterized in that there are two different types of blades, called type I (34a) and II (34b) respectively; those of type I (34a) being placed on one of the two faces of the discoidal body (28) and those of type II (34b) on the opposite face; and where the centrifugal forces generated by both types (34a and 34b) are of different magnitude. 25.- AGITATED FILM HEAT EXCHANGER, according to any one of claims 1-7 and any of group 21-23, characterized in that every two consecutive sub-chambers (2) belonging to the first chamber (29), are communicated through central segments (3), which pass through the interior of the sub-chambers that interpose between the two, and the first chamber (29) being inside a vat or housing (59); and where every two consecutive subchambers (4) belonging to the second chamber (30) communicate through the spacing between the periphery of the subchambers (2) of the first chamber (29) and the inner wall of the tank or housing (59).  26.- AGITATED FILM HEAT EXCHANGER, according to claim 25, characterized in that the modular elements it possesses all belong to a single type, called VI (61), comprising: a first thermal plate (61a); a second thermal plate (61b); one of the central segments (3) communicating two consecutive sub-chambers (2) 10 belonging to the first chamber (29), having one of its ends attached to the center of the first thermal plate (61a), and the opposite end attached to the center of the second thermal plate (61b); and an annular body (47a), fixed to the first or second thermal plate (61a, 61b) and in 15 where the modular elements (61) thus constituted are arranged in series and in the inner volume of the tank or housing (59) , so that the first chamber (29) is inside the modular elements (61) and the second chamber (30) externally and internally to said housing (59). 27 27.- HEAT EXCHANGED FILM HEAT EXCHANGER, according to any of the preceding claims, characterized in that it comprises means that hold type II removers (26) and promote their rotation. 28.- AGITATED FILM HEAT EXCHANGER, according to claim 27, characterized in that said fastening means comprise at least one rotating roller (39), on which the weight of the remover (26) rests. 29.- AGITATED FILM HEAT EXCHANGER, according to claim 27 and any of the group 9-14, characterized in that said fastening means comprise a sliding track (38), introduced into the central perforation (26a) of the remover (26 ) and subject to the modular element in which it is housed; adapting the geometry of the slide track (38) to that of said perforation, (26a) leaving a spacing between the two that allows the entry of a film of the fluid to be treated, so that the coefficient of friction is reduced. 30.- HEAT EXCHANGED FILM HEAT EXCHANGER, according to any of the preceding claims, characterized in that in the contact areas between each two adjacent contiguous modular elements, once arranged in series and approximately aligned, a sealing gasket is interposed, then being exercised a compression of the whole set of elements and thus forming the watertight chambers through which the fluids circulate. 10. 31. AGITATED FILM HEAT EXCHANGER, according to claim 30, characterized in that the sealing joints can be single (13a) and double (13b), where a space (40a, 40b is formed in the double joints (13b)) ) capable of being vented to the atmosphere, which minimizes the possibility of mixing the different fluids due to leaks or deterioration in the joints (13b). 32 32.- AGITATED FILM HEAT EXCHANGER, according to any of claims 30 or 31, characterized in that a plurality of the joining areas between adjacent modular elements are reinforced with an additional local compression by nuts (43), thus increasing the pressure on the gaskets of the seal in question and thus preventing possible leakage of the seal. 33.- AGITATED FILM HEAT EXCHANGER, according to any of the preceding claims, characterized in that the thermal plates (27) have a circular shape. 25 34.- AGITATED FILM HEAT EXCHANGER, according to any of the preceding claims, characterized in that, in case the thermal plates (27) have a striated surface, they have concentric grooves. 30 35.- HEAT EXCHANGED FILM HEAT EXCHANGER, according to any of the preceding claims, characterized in that the thermal plates (27) have a set of reinforcing rings (51), welded on their surface, so that the plate (27) acquires a greater mechanical resistance and can withstand greater pressure differences. 36.- HEAT EXCHANGED FILM HEAT EXCHANGER, according to claim 34 and any of the group 6, 9-14, 22-24, characterized in that the blades 5 have an inverse geometric shape to that of the surface of the thermal plates (27) , adapting to it and thus keeping the separation distance between both elements constant. 37.- AGITATED FILM HEAT EXCHANGER, according to any of the preceding claims, characterized in that it comprises a set of inlet and outlet mouths (31a, 32a, 31b, 32b) for the different fluids, where all of them are located in a first end of the two that has the exchanger (1), so that to disassemble it, it is not necessary to disassemble the connections between said mouths (31a, 32a, 31b, 32b) and the auxiliary installations; for this, the exchanger (1) comprises at least one inlet pipe (15) and / or at least one return pipe (14), which effect changes in direction that allow the direction of the fluid flowing through them to be reversed.