DE102012013755A1 - Heat exchanger plate unit for temperature compensation between air and water in e.g. ship, has shell parts made of plastic and connected such that fluid flows through unit along channel, which extends between inflow and discharge openings - Google Patents

Abstract

The unit (10) has a shell part (1) including a meander-like profile that forms a channel (4) between the shell part and another shell part (2) for a fluid in a connected state of the shell parts. Each shell part includes an inflow opening (5) and a discharge opening (6), where the channel extends between the inflow opening and the discharge opening. The shell parts are made of plastic. The shell parts are connected such that the fluid flows through the unit along the channel. A height of the channel is smaller than 2 mm, preferably 1 mm, preferably 0.5 mm. Independent claims are also included for the following: (1) a heat exchanger (2) a method for manufacturing a heat exchanger.

Description

The invention relates to a heat exchanger plate unit for a heat exchanger, comprising a first shell part, a second shell part, wherein at least one shell part has a profiling which forms at least one channel between the shell parts for a first fluid in a connected state of the shell parts, and at least one shell part Inlet opening and at least one outflow opening, between which extends the at least one channel, and a heat exchanger, comprising at least one heat exchanger package of a plurality of parallel arranged, interconnected plates, between each of which a passageway for a second fluid is formed.

The invention further relates to a method for producing a heat exchanger, comprising at least the steps of introducing a profiling into at least one shell part, connecting a first shell part with a second shell part to a heat exchanger plate unit having at least one channel, connecting two heat exchanger plate units to the openings of the shell parts and connecting a plurality of heat exchanger plate units to a heat exchanger package.

Heat exchangers and heat exchanger plate units for this purpose are generally known from the prior art. In such heat exchangers, a plurality of heat exchanger plate units, called plates for short, are arranged parallel next to one another, so that passage channels or gaps for air, exhaust gases, etc. arise between the plates. A temperature equalization takes place between the air and a liquid flowing through channels within the plates. The previously known plates are made of metal, since this material has very good heat conduction properties, high temperature resistance and high resistance to pressure.

From the publication WO 2008/113740 A1 Such a plate heat exchanger with a plurality of heat exchanger plate units from two interconnected shells for temperature equalization between two fluids is known, wherein the channel for the first fluid extends within a plate. Between adjacent plates, a passageway for the second fluid is formed in each case. The shells each have two, arranged on opposite sides holes, which connect the channels of adjacent plates together. Furthermore, the shells have a plurality of grooves or ribs, by means of which an uneven height of the channel is formed in the plates. At the corners of the plates in each case elevations are formed, which stabilize a connection of adjacent plates. For connecting the plates and the composite plates thereof two opposite sides are bent, which serve as a plug-in system. In addition, the plates are welded or soldered together at the holes. An alternative stabilization of plates without grooves or ribs is achieved by a knob-like spacer on a flat portion of the plate.

The publication EP 0 611 941 B1 describes still another heat exchanger from a plurality of heat exchanger plate units from two shells with a zigzag-shaped channel between the shells. The bowls and thus the plates are made of metal. For this purpose, the shells each have a plurality of straight and V-shaped ribs. The channel within a panel is bounded outwardly by the folded edge of the shells and has different heights. Furthermore, the shells each have four holes for connecting the channels, wherein the holes have a collar projecting in an alternating direction, by means of which the metal shells are soldered together.

Such plates and thus also the heat exchangers are very wide due to the material thickness of the metal plates, the shapes of the channels within the plates and the resulting distance between adjacent plates, so that in a limited volume only a few plates can be arranged. A disadvantage of such heat exchangers are on the one hand the high weight due to the metal plates and on the other hand the elaborate soldering and / or welding process for connecting the shells and plates. Furthermore, due to the hitherto known channeling in the plates with non-uniform cross-section and the resulting uneven flow, dead zones can form in the channels in which dirt is deposited. The same applies to the passageways between the plates. These are also difficult to clean and have a high flow resistance.

It is therefore an object of the invention to provide improved heat exchanger plate units and an improved heat exchanger, so that in connection with a weight saving compared to the prior art, a larger number of heat exchanger plate units can be arranged in a limited volume, and the heat exchanger has lower flow resistance and easy to is clean. It is another object of the invention to provide a method for producing such a heat exchanger.

These objects are achieved by the features of the independent claims. Advantageous developments of the invention are the subject of the subordinate claims.

The inventor has realized that the above-mentioned object can be achieved by making the shell parts from which the heat exchanger plate units are composed of a plastic. In this way, on the one hand, the plates can be produced substantially thinner than the known metal plates and, on the other hand, the profiles forming the plates in the plates can be made flatter in comparison to the prior art. The profiles can be introduced by means of simple methods in the shell parts, for example by means of embossing. The shallow channels, in turn, provide both low flow resistance for the first fluid in the channels within the plates and for the second fluid in the passageways between the plates.

The shallow channels within the plates also allow the passageways between adjacent plates to be made flat, that is, the plates can be spaced a small distance apart in the heat exchanger. Thus, a larger number of plates can be arranged in a defined volume, so that the entire heat exchanger surface or the power density is greater. The gap-shaped passageways between the plates have a low flow resistance and are also easy to clean, so that such a heat exchanger meets the relevant hygiene requirements. The lower material weight of the plastic shell parts causes otherwise a weight saving of the heat exchanger.

The plastic shell parts may be interconnected such that the first fluid only propagates along the channels through the plates. This is achieved for example by a full-surface connection, a plurality of punctiform connections and / or linear connections along the channels. To connect the shell parts can be glued together and / or welded accordingly.

The channels have, for example, an approximately rectangular cross-section, wherein at least one side of the channel is curved, that is not flat. In this way, a curvature of the channel due to a large internal pressure of the first fluid can be prevented because already curved sides deform much less than flat sides of the channel. Such shaped channels are easy to clean from the outside, ie from the passageways between the plates ago and prevent dirt deposits inside the channels in the plates. Furthermore, in this case the resistance for the first fluid when flowing through the channels is low.

A curvature of the channels can also be avoided by spacer elements are formed in the region of the channels, ie on the profiling. In the assembled state, the spacer elements of two adjacent plates are adjacent to each other or side by side, so that the channels support each other and can not bulge against each other. As a result, the shell parts or the plates are additionally stabilized.

The plates are connected together at the openings of the shell parts to form a heat exchanger package. This is done for example by means of contact surfaces, which are formed circumferentially around the openings, or by means of separate connecting elements such as sealing rings and the like.

A heat exchanger with these novel features is particularly suitable for temperature compensation between a gaseous fluid such as air and a liquid fluid such as water or a water-glycol mixture and high gas / air flow rates at very low temperature differences between the fluids. The heat exchanger thus has a high efficiency, which can be achieved by the heat capacity flows of the individual fluids, a uniform temperature distribution in the heat exchanger transverse to the main flow direction and a uniform temperature gradient along the main flow direction are coordinated. For this purpose, a constant, evenly distributed flow velocity in the main flow direction is necessary, which is ensured by the meandering channel guidance.

The very different densities and heat capacities of gases and liquids represent a particular challenge. The heat capacity flow of water is approx. 3,500 times greater in relation to air, and that of water-glycol approx. 3,200 times greater. In order to achieve high efficiency, the temperature difference from water to air along the main flow direction is kept as small and constant as possible. This is achieved by both fluids having the same heat capacity flow. In the case of heat transfer from water to air, this means that the volume flow of the water must be very small compared to the volume flow of the air.

The inventor has recognized in this regard that a highly efficient heat exchanger has the smallest possible channel cross-section for the liquid in order to achieve an adequate flow rate and a high heat transfer coefficient despite the low volume flow. Based on the flow cross section in Main flow direction would thus be the channel height in the micrometer range. However, such thin, capillary-like cross sections are easily clogged by dirt deposits, for example by corrosion residues from a connected pipe network. Adhesion forces are also noticeable at small wall spacings of the channels and additionally increase the resistance in the channels.

With a meandering channel guide, however, the channel cross-section can be adapted to the small volume flow with a flow-favorable dimension, so that a high flow velocity is achieved in the channel and, in addition, the required low velocity in the main flow direction is maintained. The flat surface-spreading distribution of a meander channel ensures a uniform flow and heat distribution over the entire surface of the heat exchanger. A constant flow velocity due to the constant channel cross-section lowers the flow resistance in the channel. By means of the channel cross-section designed for these requirements, both optimum heat transfer is achieved and the dirt deposits or slagging in the channel are reduced. For higher volume flows, several meandering channels can be executed in parallel.

Accordingly, the inventor proposes an improved heat exchanger plate unit for a heat exchanger, comprising a first shell part, a second shell part, at least one shell part having a profiling, which forms at least one channel between the shell parts for a first fluid in a connected state of the shell parts, and je Shell part at least one inflow opening and at least one drain opening, between which the at least one channel extends, wherein the two shell parts are formed from a plastic and the shell parts are connected such that the first fluid flows through the heat exchanger plate unit along the at least one channel. Such heat exchanger plate units can be formed with shallow channels so that the heat exchanger plate units can be lined up with small distances directly to each other and a large number of heat exchanger plate units can be arranged in a limited volume.

The heat exchanger plate unit comprises two shell parts. The shell parts are preferably formed in one piece. In one embodiment, the shell parts are made the same, in other embodiments, the shell parts are designed differently. Furthermore, the shell parts are preferably rectangular, in particular square, formed. A preferred embodiment provides symmetrical shell parts. Preferably, the shell parts are substantially planar, wherein at least one of the two shell parts has a profiling. For example, only one shell part or both shell parts on a profiling. Advantageously, two profiled shell parts are formed in mirror image.

Between two connected shell parts, the at least one channel for the first fluid is formed. For this purpose, the two shell parts are arranged parallel to one another and connected to one another. In one embodiment, exactly one channel is formed. Other embodiments provide more than one channel, for example two, three or four channels. For example, multiple channels are connected in parallel and / or serially. The channel or the channels are formed by the profiling of one or both shell parts. Accordingly, the concave sides of the profiling are preferably oriented in each case toward the other shell part. The profilings are embossed, for example, in the shell parts.

In a preferred embodiment, the channel over its entire length has a nearly uniform cross section, in particular a uniform height, in order to ensure the most uniform flow possible. In one embodiment with only one profiled shell part, the height of the channel corresponds to the height of the profiling of a profiled shell part. In contrast, in one embodiment with two profiled shell parts, the height of the channel corresponds to the sum of the heights of both profiles.

Advantageously, each shell part has at least two through openings, that is to say at least one inflow opening and at least one outflow opening, between which the at least one channel extends. Consequently, the openings are formed at the beginnings and ends of the channels and fluidly connected thereto. The openings are preferably formed on one side of the shell parts, advantageously in the corners. Further advantageously, the openings are each formed at the same position of the shell parts, so that they are congruent when connecting. In a preferred embodiment, round openings are provided. Other forms of openings are feasible. A diameter of the openings is adapted to the volume flow and preferably corresponds to a width of the channel. The openings are introduced, for example, in the shell parts by means of punching and / or drilling.

In one embodiment, a shell part has four holes, which are preferably arranged in the corner regions of the shell part. To realize an inflow opening and a drain opening, two of the four holes are closed, for example by means of a closure, plug or the like. The two unsealed holes then form the openings for the first fluid. Advantageously, in this embodiment, the inflow and outflow ports may be formed on either a short or a long side of a rectangular shell part or diagonally on the shell part. A composite of such shell parts plate can be flexibly adapted to external conditions of the heat exchanger, such as the position of a water connection. In the following, openings are understood as meaning in each case the unclosed holes, that is to say the inflow and outflow opening, of the shell part.

The first fluid is preferably a liquid, such as water or water-glycol mixture. The liquid advantageously flows through the inlet opening into the channel between the shell parts, through the channel and out of the drainage channel out of the channel. The direct connection between the inflow and outflow openings forms the main flow direction of the liquid. However, the liquid in the channel can partially flow in different flow directions. The main flow direction of the first fluid is preferably opposite to the flow direction of a second fluid, which flows around the plates.

According to the invention, the two shell parts are made of a plastic. The use of a heat exchanger at moderate temperatures, such as in the air and air conditioning technology, allows the execution of the shell parts of a different material than the previously known metals. In addition to a weight saving, such a material offers the advantage that the plates can be produced and processed with simple methods. Furthermore, plastic is corrosion resistant to most aggressive media. When cooling air, condensate often accumulates, which has a corrosive effect in combination with contaminated air. Deeper cooling results in layers of ice that are easier to peel off from smooth plate surfaces, or even plastic surfaces. A complex and expensive coating, as in metal heat exchangers, is advantageously not necessary for plastic. Therefore, a heat exchanger with shell parts made of plastic is particularly suitable for use in coastal regions, on ships, in the chemical, food and / or pharmaceutical industry. Likewise, plastic as a material is much cheaper than metal, especially compared to the copper often used.

The plastic shell parts are produced for example by means of known methods such as thermoforming, in particular thermoforming, blow molding and / or injection molding. In particular, a twin-sheet thermoforming process is suitable in which two shell parts are pulled simultaneously and pressed together in a still soft state and connected. As a result, advantageously, a separate operation for connecting the shell parts can be saved. The same applies to the blowing process, in which a plate with the hollow channels of two shell parts can be produced in one operation.

Furthermore, according to the invention, the shell parts are connected such that the first fluid flows through the heat exchanger plate unit along the at least one channel. For connection, the shell parts are preferably connected together in the flat areas. In one embodiment, the connection of the shell parts over the entire surface is formed outside the channels, for example over an entire flat surface of the shell parts, that is, with the exception of the regions of the profilings. In another embodiment, the shell parts are connected by means of a plurality of punctiform connections outside the at least one channel. Yet another embodiment provides that the shell parts are connected by means of a plurality of linear connections along the at least one channel. These compounds according to the invention ensure that the liquid substantially propagates in and along the channels between the shell parts. Preferably, the respective connection of the shell parts is designed as an adhesive bond and / or welded joint. These compounds are easy to carry out especially with plastic shell parts. In addition, the shell parts can still be bolted together and / or otherwise connected.

In one embodiment, the profiles and thus also the channel or the channels are formed meander-shaped. In this case, a plate may have one or more meanders connected in parallel in the main flow direction. A meandering channel has at least one loop, but preferably several, for example 10, 20, 30 or more. With the number of loops and the associated area of a plate increases the efficiency of the heat exchanger. Between the loops, the channel preferably has straight sections with changing flow directions. Preferably, the meandering channel is symmetrical. The respective actual orientation of the channel and thus an instantaneous flow direction of the liquid in the channel between the inflow and the outflow opening preferably deviate from the main flow direction.

At low flow rates, a small channel cross-section is necessary to ensure a sufficiently high velocity and turbulent flow for to form a good heat transfer. For large-area plate-shaped Wärmetaucherplatteneinheiten this is advantageously achieved by a meandering channel guide. Thus, a good flow and heat distribution is achieved in the margins and corners. In a direct, so not meandering, channel guide in the main flow direction, the flow rate would be too small and the risk of the formation of dead water zones and deposits would be given.

In another, adapted to larger volume flow embodiment, a parallel, non-meandering channel guide is provided. The channel in this case has a plurality of mutually parallel sub-channels. The sub-channels are connected to each other at the ends by means of a collecting channel. A collecting channel advantageously extends between the openings arranged on one side of the shell part. The parallel channels can run both transversely and in the main flow direction.

Another special feature of the invention is that the channels are made very flat due to the formation of plastic shell parts. The height of a channel is preferably less than 2 mm, more preferably less than 1 mm, most preferably less than 0.5 mm. This allows a relatively flat outer surface of the individual plates with only slightly protruding profilings. As a result, the flow resistance of the gas flowing past between the plates is significantly reduced compared to known heat exchangers. By means of the shallow channels or the resulting thin plates, it is possible to arrange a larger number of plates in a limited volume.

The plate thickness can be reduced in addition to the flat channel shape in addition by means of a low material thickness of the shell parts. In this case, the lower the material thickness, the thinner the plate can be performed. In one embodiment, the height of the channel is at most five times, preferably at most three times, more preferably at most the single and most preferably half the material thickness of a shell part. The low material strength also has a favorable effect on the heat transfer and reduces the disadvantage of poor heat conduction of plastic, so that the effectiveness of the heat exchanger against a metal heat exchanger is not affected.

The channel has an approximately rectangular cross-section in one embodiment. An aspect ratio of the rectangular channel cross section is advantageously 5: 1 to 40: 1, preferably 10: 1 to 25: 1. In another embodiment, the cross section of the channel is curved at least on one side. In other words, the channel has at least one curved side. Advantageously, an aligned to an adjacent plate side of the channel is curved. Further advantageously, both sides of the channel facing the adjacent plates are curved. One embodiment provides for an approximately circular channel cross-section, which is formed, for example, from two profilings which are arcuate in cross-section.

Due to the pressure prevailing by the flow in the channel internal pressure, the shell parts can deform in the region of the channels above a certain internal pressure, in particular bulge outward. This can be avoided on the one hand by the side walls of the channel are already curved or arched outwards. An already arched or curved side of the channel is much more stable, that is, experiences a much lower additional curvature, as a flat side.

Another embodiment provides for the stabilization of the channels, that at least one spacer element is formed on the channel in the region of the profiling. Advantageously, in each case a plurality of spacer elements are formed on the profiling of a shell part, wherein the spacer elements are preferably carried out the same. The spacer elements are preferably formed on an outer side of the channels. In other words, the spacer elements are arranged on the side facing away from the channel, convex side of the shell part or aligned respectively connected plates to the adjacent plate out. Furthermore, the spacer elements are preferably formed uniformly spaced on the channels. Preferably, the spacer elements are formed on the straight sections between the loops of a meandering channel. The spacer elements serve to support each other two adjacent plates. In the assembled state of several plates, the spacer elements of adjacent plates may abut each other. From an internal pressure in the channel of about 2 bar it bulges outwards. However, this bulge is prevented by the adjacent spacers of the adjacent plate, wherein the pressure of the channels is delivered to the respective adjacent plate.

The spacer elements have for example a round and / or elongated shape. Elongated spacer elements preferably extend over one third of the width of the channel, more preferably over half the width, and most preferably across the entire width of the channel. Preferably, the spacer elements are formed without corners and edges to a flow resistance between the Do not negatively influence plates and avoid deposits on the spacer elements. In an embodiment with elongated, for example, approximately rectangular spacer elements, a longitudinal extent of the at least one spacer element is aligned obliquely to a main flow direction of the first fluid in the channel. The main flow direction of the first fluid is aligned counter to the flow direction of the second fluid, so that the longitudinal extent is also aligned obliquely to the flow direction of the second fluid. An angle of attack between the longitudinal extension of the spacer elements and the main flow direction of the first fluid is preferably less than 45 °, more preferably less than 25 °, even more preferably less than 15 ° and most preferably between 5 ° and 10 °. One embodiment provides for crossing spacers of adjacent plates.

In an embodiment with round, for example knob-like spacer elements, these are advantageously arranged on one side of the channel, more preferably on the channel edge. Preferably, the knob-like spacer elements are arranged on adjacent plates laterally offset on the channels. When supporting adjacent plates, the knobs are advantageously on each of the other side of the channel. In a region of the channel between the spacer elements, which is therefore not supported, a curvature of the channel is deliberately allowed in this embodiment, so that the pressure remains in the shell parts and is not passed on to adjacent plates.

Adjacent plates in a heat exchanger package or in the heat exchanger are preferably connected to one another. This connection of the plates is formed either directly or indirectly. To realize a direct connection of two plates, the openings of the shell parts each have at least one contact surface. Preferably, the plates are then connected together at the contact surfaces of the shell parts, in particular adhesively bonded and / or welded. Advantageously, a contact surface is formed at each opening of the shell parts.

The contact surface is preferably formed circumferentially around the opening, for example as a nozzle and / or tubular approach. The approach preferably protrudes in the same direction or on the same side of the shell part as the profiling. The contact surface can be advantageously introduced in one step with the embossing of the profiling in the shell parts. Advantageously, the contact surface is thus formed integrally with the shell part. In order to ensure a stable connection of adjacent plates to the contact surfaces, a height of the contact surface is preferably equal to or higher than a height of the profiling.

For realizing an indirect connection of two plates, at least one connecting element is provided in the region of the openings of the shell parts. The connecting element is formed, for example, as a coupling piece with a sealing ring, which is inserted into the openings and the shell parts are attached thereto.

The scope of the invention also includes a heat exchanger, at least comprising a heat exchanger package of a plurality of parallel arranged, interconnected plates, between each of which a passageway for a second fluid is formed, wherein the plates are formed according to the invention as described above heat exchanger plate units. Such a heat exchanger with the plates according to the invention is preferably lightweight with a large number of plates in a limited volume and has a very low flow resistance in the through channels.

A heat exchanger package includes a plurality of plates. The plates are arranged parallel to each other and connected to each other. According to the above-described embodiment of the shell parts made of plastic, the flat plates can advantageously be arranged side by side with a small distance. Adjacent plates are connected to each other at the openings of the shell parts, for example at the contact surfaces and / or by means of connecting elements.

The channels of the plates are preferably fluidly connected to one another via the congruently arranged openings of the shell parts. The juxtaposed and connected openings form two tubular channels through the heat exchanger package. These tubular channels can also be connected to a water inflow and outflow.

Between two adjacent plates in each case a gap-shaped passageway for the second fluid is formed. The width of a passage channel substantially corresponds to the distance between two adjacent plates and is preferably in the range of a few millimeters. The width of the through channels is up to ten times the height of the channel in the shell parts, most preferably three times the height of the channel, or less. Further advantageous is a cross section of the passage channel 30 to 300 times larger than the cross section of the channel in the shell parts, preferably 50 to 150 times larger. One preferred ratio of these dimensions is between 1: 6 and 1: 2, more preferably between 1: 4 and 4:10.

The second fluid is preferably a gas, usually air. The direction of flow of the gas through the passage channels is preferably aligned opposite to the main flow direction of the liquid, wherein a flow direction of the liquid is aligned in the straight portion of the meandering channel transverse to the flow direction of the gas. Between the fluids there is a heat exchange. Due to the shallow formation of the channels and the thus almost smooth surfaces of the shell parts, there is less flow resistance in the through channels than in previously known heat exchangers, so that high flow velocities can also be achieved.

The passageways are easy to clean as there are no structural obstacles to access, such as depressions and / or transverse tubes. The heat exchanger according to the invention thus fulfills the respective hygiene regulations. This heat exchanger shows particular advantages in the case of aggressive and polluted media, since the heat exchanger is both corrosion-resistant and easily accessible for cleaning purposes. For example, the heat exchanger is insensitive to chemically contaminated exhaust air, so for example ammonia and / or nitrogen oxide-containing exhaust gases. This opens up a broad field of application, for example in agriculture, the chemical, pharmaceutical and food industries, but also in environmental technology.

The spacer elements of adjacent plates are preferably arranged in an intersecting manner. By means of the spacer elements, on the one hand, a constant spacing of the plates is maintained and, on the other hand, the spacer elements serve to mutually support the channels of adjacent plates. Due to the channel internal pressure, the channels can bulge outward, this curvature being limited in each case by the adjoining spacer elements. In order to achieve a better contact surface of the spacer elements, these are therefore advantageously at an angle to each other, in particular crosswise, arranged.

For further stabilization of the plates, a reinforcing plate is arranged parallel to the plates on at least one outer side of the heat exchanger package. Preferably, a reinforcing plate is arranged on both outer sides. The reinforcing plates are advantageously formed of a stiffer material such as the plates, for example metal. Thus, an internal pressure of the channels to the reinforcing plates, which can be held together by tie rods for example, are derived. In another embodiment, instead of the reinforcing plates, a frame receives the compressive forces.

The invention further relates to a method for producing a heat exchanger according to the invention described above, comprising at least the steps of introducing a profiling into at least one shell part, connecting a first shell part with a second shell part to a heat exchanger plate unit having at least one channel, connecting two heat exchanger plate units at the openings the shell parts and connecting a plurality of heat exchanger plate units to a heat exchanger package. The method is characterized in that the shell parts are glued together and / or welded.

The shell parts are preferably made of a plastic by means of a simple process, for example a deep drawing process. The profiles and the openings are advantageously introduced in a common step in the shell parts, embossed, for example. The shell parts are preferably made with a material thickness of a few millimeters.

In a further step, two shell parts are connected to a plate, so that the openings of the shell parts are congruent. In this case, the shell parts, for example, are glued together over the entire surface, so that the liquid only flows through the composite plate along the channel. If both shell parts have a profiling, this is preferably mirror-inverted. Between the shell parts, that is in the field of profiling, the channel is formed. Due to the small material thickness of the shell parts and the shallow channels, the plate thus formed is advantageously substantially flat and thin.

A plurality of plates is assembled in a further step to a heat exchanger package. For this purpose, the individual plates are connected to one another in the region of the openings, for example glued to the contact surfaces or connected by means of additional connecting elements. A finished heat exchanger package is advantageously used in a frame and / or a housing of the heat exchanger. For additional fixation, the sides of the plates can be arranged in retaining rails. In one embodiment, the retaining rail has a rake-shaped leg with protruding teeth, which are designed to match the spacing of the plates. The teeth protrude into the passageways between the plates.

With the number of plates can the size of the heat exchanger and thus its performance be varied. Larger heat exchangers can also be joined together from a plurality of heat exchanger packages, for example by juxtaposing and / or stacking the heat exchanger packages.

Overall, with the features described above, conventional plate-type heat exchangers can be outperformed in terms of efficiency, performance, resistance and cost. Thus, these heat exchangers are particularly suitable for heat recovery systems, especially in ventilation and / or air conditioning systems, where in addition to high efficiency and low resistances, hygienic designs and low volume are required or prescribed by standards. For other applications, such as in low-temperature heating with, for example, 30 ° C flow temperature, the waste heat, district heating and / or room air cooling this heat exchanger offers through the tailored specific construction, advantages and efficiency.

In the following the invention with reference to the preferred embodiments with reference to the figures will be described in more detail, with only the features necessary for understanding the invention features are shown.

They show in detail:

1 a schematic front view of a shell part in a first embodiment;

2 : a schematic representation of the flow directions in a heat exchanger;

3 FIG. 2 is a schematic cross-sectional view of a heat exchanger plate unit in a first embodiment; FIG.

4 a schematic cross-sectional view of a heat exchanger plate unit in a further embodiment;

5 a schematic representation of a heat exchanger package;

6 an enlarged detail A of the heat exchanger package according to the 5 ;

7 FIG. 2 is a schematic side view of the heat exchanger package according to FIG 5 ;

8th a schematic front view of a shell part in a further embodiment;

9 FIG. 2: a schematic representation of the shell part according to the embodiment of FIG 8th ;

10 an enlarged detail B of the shell part according to the 8th ;

11 a section of a cross-sectional view of two adjacent heat exchanger plate units in the region of the spacer elements;

12 a schematic representation of a heat exchanger package with a housing;

13 an enlarged detail C of the heat exchanger package according to the 12 ;

14 a schematic front view of a shell part in yet another embodiment;

15 a schematic front view of a heat exchanger plate unit with double channel guide; and

16 FIG. 2: a schematic representation of the flow directions in the heat exchanger plate unit according to FIG 15 ,

The 1 shows a schematic front view of a shell part 1 in a first embodiment. The shell part 1 is made according to the invention of a plastic by means of a deep-drawing process. Furthermore, the shell part 1 rectangular and essentially flat with a meandering profiling 3 educated. Here, the meandering shape of the profiling 3 three loops, between which straight sections are formed with a uniform width. The profiling 3 is opposite to the remaining flat surface of the shell part 1 on one side of the shell part 1 increased educated. Under the profiling 3 is at two interconnected shell parts 1 . 2 a corresponding meandering channel for a first fluid, such as water, formed (see 3 and 4 ). In the 1 is the raised side of profiling 3 or the outer side of the channel 4 shown.

Furthermore, the shell part comprises 1 an inflow opening 5 and a drain hole 6 , in the following also with openings 5 . 6 summarized. The openings 5 . 6 are on one side of the rectangular shell part 1 each arranged in a corner and formed as round holes. Between the openings 5 . 6 runs the channel 4 or the meandering profiling 3 , where the channel 4 fluidic with the openings 5 . 6 connected is. Here are the openings 5 . 6 as inflow and outflow for one through the canal 4 flowing fluid. A direct connection of the openings 5 . 6 sets a main flow direction W of the water in the channel 4 firmly (see 2 ).

At the openings 5 . 6 is each a contact surface 7 educated. According to the embodiment of the 1 are the contact surfaces 7 around the openings 5 . 6 designed as a tube-like approach. The contact surfaces 7 are used for contacting and connecting with another shell part of an adjacently arranged plate (see 5 to 7 ).

The shell part 1 still includes a variety of spacers 8th which is on the outside of the profiling 3 are arranged. The spacer elements 8th are elongated, that is approximately rectangular with rounded corners formed. On the straight sections of the profiling 3 are each four evenly spaced spacers 8th arranged. Here is a longitudinal extension of the spacer elements 8th oblique to the main flow direction W in the channel 4 aligned. An angle of attack α of the spacer elements 8th to the main flow direction W is between 5 ° and 10 °. Furthermore, the spacer elements extend 8th almost over the entire width of the profiling 3 ,

In the 2 the flow directions are shown schematically in a heat exchanger. The main flow direction W of the first fluid, for example water, runs counter to a flow direction L of a second fluid, for example air. The water flows through the meandering channel of a plate (see 5 ) in the main flow direction W, wherein at the straight portions of the meander, the respective flow direction of the water is aligned transversely to the flow direction L of the air. The respective direction of flow of the water is marked with an arrowed dashed line. On the other hand, the air flows between the plates through the through channels (see 5 and 7 ) in the opposite flow direction L or transversely to the water in the straight sections.

The 3 shows a schematic cross-sectional view of a heat exchanger plate unit 10 , also with plate 10 denotes, in a first embodiment along a sectional plane AA 1 , The plate 10 comprises a first shell part 1 and a second shell part 2 leading to the plate 10 are connected. Here are the shell parts 1 . 2 each flat connected to each other at the flat areas, for example glued, so that the water along the channel 4 through the plate 10 flows. In this embodiment, the first shell part corresponds 1 in the 1 shown shell part 1 , Furthermore, the second shell part 2 identical to the first shell part 1 educated. The same components are identified by the same reference numerals. A detailed description of components already described is therefore omitted. Between the shell parts 1 and 2 below the profiles 3 is the channel 4 educated. In this embodiment, the channel 4 over its entire length a uniform height. The openings 5 . 6 the two shell parts 1 . 2 are arranged congruently. The height of the contact surfaces 7 the shell parts 1 . 2 corresponds in each case to the height of the profiling plus the height of the spacer elements 8th so that the contact surfaces 7 and the spacer elements 8th to train a level. In this embodiment, the height of the channel corresponds 4 about four times the material thickness of the shell parts 1 . 2 ,

Another embodiment of the heat exchanger plate unit 10 is in the 4 shown. The 4 shows a schematic cross-sectional view of the plate 10 along the cutting plane AA 1 with differently shaped shell parts 1 and 2 , The profiled shell part 1 corresponds to the embodiment of the 1 and 3 , In contrast, the other shell part 2 unprofiled, so even, trained. Thus, the channel becomes 4 only from the first shell part 1 educated. In this embodiment with only one profiled shell part 1 indicates the channel 4 only half the height of the canal 4 as in the version with two profiled shell parts 1 . 2 on.

The 5 shows a schematic representation of a heat exchanger package 20 , The heat exchanger package 20 comprises a plurality of parallel juxtaposed and connected plates 10 according to the embodiment of the 3 , each with two profiled shell parts. The plates 10 are at the contact surfaces 7 at the openings 5 . 6 bonded. In the 6 is an enlarged detail A of the heat exchanger package 20 in the area of the inflow opening 5 shown. Here it can be seen that the inflow openings 5 the plates 10 are arranged congruently, so that a tubular inflow channel as a fluidic connection between the plates 10 is formed, through which the water in the channels 4 can flow in and out again.

Adjacent plates 10 lie on the spacer elements 8th to each other. Here are the angle of the spacer elements 8th neighboring plates 10 each aligned alternately, so that the largest possible and thus stable bearing surface is formed. The contacting spacer elements 8th prevent also a curvature of the channel 4 due to an excessive internal pressure and pass this internal pressure to the next plate 10 from. For further stabilization of the heat exchanger package 20 is on the outer sides in each case a reinforcing plate 21 arranged here, for the sake of clarity, only a rear reinforcing plate 21 is shown. From the reinforcement plates 21 will be the pressure of the plates 10 added. This is the reinforcing plate 21 from a harder material like the plates 10 trained, for example steel.

Between two plates 10 each is a passageway 11 educated. Through the passageways 11 the air flows through the heat exchanger package 20 , The passageways 11 are in particular in the 7 shown. The 7 shows a schematic side view of the heat exchanger package 20 according to the 5 , Here are on the one hand, the passageways 11 between the plates 10 as well as the contact surfaces 7 and the spacer elements 8th on which the plates 10 are glued or abut each other, shown. The passageways 11 have a low flow resistance. In addition, it can be seen that the individual plates 10 are very flat and arranged at a small distance from each other.

In the 8th is a schematic front view of a shell part 1 shown in a further embodiment. The shell part 1 of the 8th differs from the shell part 1 in the embodiment of the 1 only in the design and arrangement of the spacer elements. Same components of the shell parts 1 are therefore identified by the same reference numerals. A detailed description of components already described will be omitted. The spacers are in the embodiment of 8th as pimples 9 formed and on a single side of the meandering channel 4 each arranged on the straight sections. Here are the nubs 9 equally spaced from each other. Furthermore, the pimples differ 9 in their function of the elongated spacer elements (see 12 ).

The 9 shows a schematic representation of the shell part 1 according to the embodiment of the 8th , A further enlarged detail B of the shell part 1 is in the 10 shown. Detail B shows the shell part in the region of the inflow opening 5 , Here is in particular the circumference around the inflow opening 5 arranged contact surface 7 shown. The contact surface 7 is a tube-like approach to the inflow opening 5 formed with an angled end, so that a contact surface is formed. At these contact surfaces 7 The plates can be glued to connect.

In the 11 is a section of a cross-sectional view of two adjacent heat exchanger plate units in the region of the knob-like spacer elements according to the 8th shown. The section shows the channels 4 the shell parts 1 . 2 with the pimples 9 , The pimples 9 are each offset on the side of the channels 4 arranged. In the connected state shown here are the knobs 9 of a shell part 1 on the other shell part 2 and vice versa, with the nubs 9 do not contact. Basically, the nubs 9 the distance between two adjacent plates 10 preserve. Opposite the spacer 8th , which additionally causes a stiffening of the channel wall and prevents bulging at high internal pressure, this embodiment leaves the curvature of the channel 4 in the middle between the pimples 9 however, too, so that the compressive forces are not transferred to adjacent plates The curvature of the channels 4 is shown in dashed lines. These are the pimples 9 at the extreme edge of the canal 4 positioned where hardly any expansion takes place. The pimples 9 are designed around, so this on the opposite shell part 1 . 2 can slide as soon as through the curvature of the channel 4 an oblique position of the pimples 9 established. This embodiment is intended for lower internal pressures and sufficient material stiffness to accommodate the reinforcing plates described below 12 ) save.

In the 12 is a schematic representation of a heat exchanger package 20 with a housing 31 shown. The embodiment of the heat exchanger package 20 corresponds to the embodiment of the 5 , To the heat exchanger package 20 is the case 31 arranged and two reinforcing plates on two opposite outer sides of the housing 31 , With the inventive embodiment of the shell parts and the plates, the heat exchanger package 20 with a large number of flat, closely spaced plates within the defined volume of the housing 31 educated.

In this version, the heat exchanger package 20 or the housing 31 cuboid shaped. The reinforcing plates of the housing 31 each have two opposite openings, which have an air inlet 32 and an air outlet 33 for a gas, in particular air. The air flows through the heat exchanger package 20 That is, through the passageways between the individual plates. Next are on the case 31 on two other opposite side surfaces in each case two mirror-inverted water flows 34 and drains 35 formed, which with the inflow openings 5 and the drainage holes 6 the plates are connected. The inflows and outflows are arranged so that the main flow direction W of the water in the plates is oriented opposite to the flow direction L of the air in the through channels (see 2 ). When flowing through the heat exchanger takes place a temperature exchange between the air and the water.

In the 13 is an enlarged detail C of the heat exchanger package 20 with the housing 31 according to the 12 shown. Detail C shows a section of the heat exchanger package 20 in the area of a corner of the air inlet 32 , So that the individual plates and passageways can be seen. The plates of the heat exchanger package 20 are glued together on one side and are for additional stabilization on the opposite side respectively in the interstices of a retaining rail 36 arranged. The retaining rail 36 has a plurality of teeth, in the spaces between which the plates are arranged and are fixed so. As a result, a movement of the plates in the air flow can be prevented.

In the 14 is yet another embodiment of a shell part 1 shown. The shell part 1 is different from the ones in the 1 to 13 shown embodiments in the channel guide and in the formation of the openings 5 . 6 , Incidentally, the function and operation of this further embodiment corresponds to the embodiments described so far. The same components are identified by the same reference numerals. A detailed description of components already described is therefore omitted. In the following, only the differences of the embodiments will be described.

The shell part 1 of the 14 is rectangular with four holes each in the corner areas. Two of the holes of the cup part 1 , are by means of a lock 4c locked. The other two holes form the inflow opening 5 and the drainage hole 6 of the canal 4 , In this training can be chosen arbitrarily, which closed the four holes or as openings 5 . 6 be used. To a uniform flow through the channel 4 to reach, here is a diagonal allocation of the inflow opening 5 and the drainage hole 6 executed.

Between the openings 5 . 6 extends the channel 4 for the water. In this embodiment, the channel is 4 formed with a parallel channel guide. Accordingly, the channel has 4 a plurality of parallel aligned sub-channels 4a on. The subchannels 4a are each on the short sides of the shell part 1 So at the beginnings and ends of the subchannels 4a , by means of a collecting channel 4b connected with each other. The main flow direction W of the water also extends from the inflow opening in this embodiment 5 to the drainage hole 6 ,

The 15 shows a schematic front view of a heat exchanger plate unit 10 with double meandering channel guide. In this embodiment, the plate comprises 10 two separate meandering channels, namely a first channel 4.1 and a second channel 4.2 , The individual channels 4.1 and 4.2 basically correspond to the channel of the embodiment of 1 , The same components are identified by the same reference numerals. A detailed description of components already described is therefore omitted. In this dual channel guide are the two channels 4.1 and 4.2 connected in parallel. By this embodiment, two heat exchanger packets, each having a channel in the plates can be replaced by a heat exchanger package with two channels in the plates. In this way, an additional frame can be saved in the housing of the heat exchanger between the heat exchanger packages.

The flow directions W and L of the fluids in the heat exchanger of 15 are in the 16 shown. These basically correspond to the intersecting flow directions according to the 2 , with two meandering flows in the plate 10 available. According to the same scheme, three or more meandering channels can be switched in parallel.

Overall, the invention provides a heat exchanger plate unit for a heat exchanger, comprising a first shell part, a second shell part, wherein at least one shell part has a profiling, which form at least one channel for a first fluid in a connected state of the shell parts, and at least one inlet opening per shell part and at least one outflow opening, between which the at least one channel extends, proposed, wherein the two shell parts are formed from a plastic and the shell parts are connected such that the first fluid flows through the heat exchanger plate unit along the at least one channel. Further, a heat exchanger, at least comprising a heat exchanger package from a plurality of parallel arranged, interconnected heat exchanger plate units, between each of which a passageway is formed, proposed, and a method for producing a heat exchanger according to the invention, wherein the shell parts are glued together and / or welded.

Although the invention has been further illustrated and described in detail by the preferred embodiment, the invention is not limited by the disclosed examples, and other variations can be derived therefrom by those skilled in the art without departing from the scope of the invention.

LIST OF REFERENCE NUMBERS

1

first shell part

2

second shell part

3

profiling

4

channel

4.1

first channel with double ducting

4.2

second channel with double ducting

4a

subchannel

4b

collecting duct

4c

shutter

5

inflow opening

6

drain opening

7

contact area

8th

spacers

9

burl

10

Heat exchanger plate unit

11

Through channel

20

Heat exchanger package

21

reinforcing plate

31

casing

32

air intake

33

air outlet

34

water supply

35

water drainage

36

retaining rail

L

Flow direction of the air

W

Main flow direction of the water

α

angle of attack

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• WO 2008/113740 A1 [0004]
• EP 0611941 B1 [0005]

Claims (17)

Heat exchanger plate unit ( 10 ) for a heat exchanger, comprising: 1.1. a first shell part ( 1 1.2. a second shell part ( 2 ), wherein at least one shell part ( 1 . 2 ) a profiling ( 3 ), which in a connected state of the shell parts ( 1 . 2 ) at least one channel ( 4 ) between the shell parts ( 1 . 2 ) for a first fluid, and 1.3. each shell part ( 1 . 2 ) at least one inflow opening ( 5 ) and at least one drain ( 6 ), between which the at least one channel ( 4 ), 1.4. the two shell parts ( 1 . 2 ) are formed of a plastic and 1.5. the shell parts ( 1 . 2 ) are connected such that the first fluid is the heat exchanger plate unit ( 10 ) along the at least one channel ( 4 ) flows through. Heat exchanger plate unit ( 10 ) according to the preceding claim 1, characterized in that the connection of the shell parts ( 1 . 2 ) outside the at least one channel ( 4 ) is formed over the entire surface. Heat exchanger plate unit ( 10 ) according to the preceding claim 1, characterized in that the connection of the shell parts ( 1 . 2 ) from a multiplicity of punctiform connections outside the at least one channel ( 4 ) is trained. Heat exchanger plate unit ( 10 ) according to the preceding claim 1, characterized in that the connection of the shell parts ( 1 . 2 ) of a plurality of linear connections along the at least one channel ( 4 ) is trained. Heat exchanger plate unit ( 10 ) according to one of the preceding claims 1 to 4, characterized in that the connection of the shell parts ( 1 . 2 ) is designed as an adhesive bond and / or welded joint. Heat exchanger plate unit ( 10 ) according to one of the preceding claims 1 to 5, characterized in that the at least one channel ( 4 ) is meander-shaped. Heat exchanger plate unit ( 10 ) according to one of the preceding claims 1 to 6, characterized in that a height of the at least one channel ( 4 ) is less than 2 mm, preferably less than 1.0 mm, more preferably less than 0.5 mm. Heat exchanger plate unit ( 10 ) according to one of the preceding claims 1 to 7, characterized in that a cross-section of the at least one channel ( 4 ) in the flow direction of the at least one channel ( 4 ) is curved at least on one side, preferably oval or circular, is formed. Heat exchanger plate unit ( 10 ) according to one of the preceding claims 1 to 8, characterized in that on the profiling ( 3 ) at least one shell part ( 1 . 2 ) at least one spacer element ( 8th ) is trained. Heat exchanger plate unit ( 10 ) according to the preceding claim 9, characterized in that between a longitudinal extension of the at least one spacer element ( 8th ) and a main flow direction (W) of the first fluid in the at least one channel (FIG. 4 ) an angle of attack (α) of less than 45 °, preferably less than 25 °, more preferably less than 15 ° and most preferably between 5 ° and 10 °, is formed. Heat exchanger plate unit ( 10 ) according to one of the preceding claims 1 to 10, characterized in that the openings ( 5 . 6 ) of the shell parts ( 1 . 2 ) at least one contact surface ( 7 ) for connection to a further heat exchanger plate unit ( 10 ) exhibit. Heat exchanger plate unit ( 10 ) according to one of the preceding claims 1 to 11, characterized in that at least one connecting element for connecting two heat exchanger plate units ( 10 ) in the area of the openings ( 5 . 6 ) of the shell parts ( 1 . 2 ) is provided. Heat exchanger, at least comprising: 13.1. a heat exchanger package ( 20 ) of a plurality of parallel, interconnected plates, between each of which a passageway ( 11 ) is formed for a second fluid, characterized in that 13.2. the plates as heat exchanger plate units ( 10 ) are formed according to one of the preceding claims 1 to 12. Heat exchanger according to the preceding claim 13, characterized in that two adjacent heat exchanger plate units ( 10 ) at the openings ( 5 . 6 ) of the shell parts ( 1 . 2 ) are interconnected. Heat exchanger according to one of the preceding claims 13 to 14, characterized in that the spacer elements ( 8th ) of adjacent heat exchanger plate units ( 10 ) are arranged crossing one another. Heat exchanger according to one of the preceding claims 13 to 15, characterized in that at least one outer side of the heat exchanger packet ( 20 ) a reinforcing plate ( 21 ) parallel to the heat exchanger plate units ( 10 ) is arranged. Method for producing a heat exchanger according to one of the preceding claims 13 to 16, comprising at least the steps: 17.1. Introduction of a profiling ( 3 ) in at least one shell part ( 1 . 2 17.2. Connecting a first shell part ( 1 ) with a second shell part ( 2 ) to a heat exchanger plate unit ( 10 ) with at least one channel ( 4 ), 17.3. Connecting two heat exchanger plate units ( 10 ) at the openings ( 5 . 6 ) of the shell parts ( 1 . 2 ) and 17.4. Connecting several heat exchanger plate units ( 10 ) to a heat exchanger package ( 20 ), characterized in that 17.5. the shell parts ( 1 . 2 ) are glued together and / or welded together.

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