WO1997049962A1

WO1997049962A1 - Heat exchanger

Info

Publication number: WO1997049962A1
Application number: PCT/EP1997/003035
Authority: WO
Inventors: Aloysius Dickgreber
Original assignee: Dickgreber, Johannes
Priority date: 1996-06-22
Filing date: 1997-06-12
Publication date: 1997-12-31
Also published as: AU3434897A; DE19624937A1

Abstract

As a novel heat exchanger (1), the proposal is for a device in which the two mutually separated fluid flow chambers (18, 10b) operated on the cross-flow or counter-flow system in a bionic manner penetrate mutually intensively with the best possible heat transfer area. The box-like or hollow cylindrical flow chamber (18) of the one fluid is penetrated by the flow chamber of the other fluid, which consists of helically structured pipes or hoses or conjoined helical bunches thereof or superhelically wound bunches of pipes or hoses. The proposed heat exchangers may be used, for instance, in heating boilers, gas-gas recuperators, air heaters and waste water through-flow coolers.

Description

ζ ^~ HEAT EXCHANGER

As heat transfer walls in heat exchangers, profiled or non-profiled, planar structural structures have hitherto been known.

or smooth or profiled, straight pipes. In the case of tubular heat exchangers e.g. when using

/ Cr in a boiler, the heating gas is usually led into the pipes and the water is passed in a cross-flow or counter-flow to the outside of the pipes. With such a construction

The heat transfer promoting turbulence in the guided outside the tubes of heat transport fluid 20 are not optically tion _££> timal which results of the device in a non-optimized or non-optimized compactness of material economy. The invention relates to an apparatus for heating a heat transfer fluid, in which a heat supply fluid and a heat transfer fluid under counter-current or cross-flow zuei- "lζ ^~ Nander a heat exchanger to flow through with separate for the delivery of fluid and the transport fluid fluid flow spaces. The particular novel feature of the invention

HO heat exchanger is that the two separate fluid flow spaces penetrate each other intensively, ^ i> whereby in this invention an o p t i m a l e W a r m a u a g a n g s f l a c h e, the physically ideal operating possibility of the g e g e n s t r o m e s of the O

C ^ Tist realizes fluids and an optimal fluid turbulation in both fluid flow spaces with minimized pressure loss, which results in an overall compactness and therefore a small size for a countercurrent device. The invention presented in this patent application is a bionic. This means that the model created for this invention in nature has been optimized in terms of function and material economy in the evolution of the living.

In my first bionic, thermal engineering invention, which was registered for a patent on December 11th, 1995, it was used

20th

Structure of the gasturbulatory pulmonary alveolar duct as a model ("Invention L").

2 $ ~ The system of heat-exchanging arteries and veins in the feet of the gull ("Invention M") was used for the invention presented in this patent application. the helical structures of DNA and the structure of the wintry vegetation cover of the Atlantic raised bogs as models.

7 ^ In the vein system of the gull's foot, the widely branched arteries and veins are so closely and intensely surrounded that the heat that flows into the foot with the arterial blood is almost

H ° completely passes into the cold stream of venous blood, i.e. returns to the body insulated with feathers. ty $ ^" The cooled, arterial blood transports the oxygen into the toe area of the gull's foot and is still kept at a minimum temperature so that the gull's toes do not die. The highly efficient heat exchange system of the gull's foot is ζ ^~ ST the reason why gulls spend hours in the freezing cold Can stand water without cooling. If the object presented here is used as a heat exchanger between a liquid and a gas, then IQ can be combined with "Invention M" and integrated on the gas side in "Invention M". This makes sense because gas is usually less

/ S ^"

Has heat capacity than the liquid used and because of the lower interactions of the

7 _. 0 gas particles quickly form heterogeneous movement zones with one another in the gas, that is to say stationary peripheral, heat-insulating gas layers. Such peripheral gas layers are permanently in the subject of "Invention L" due to the design due to periodic turbulence pulses.

7) 0 broken and swirled.

In the presented W ä exchanger - τζ ^~ E rfindung has a of at least two but preferably seven tubes or hoses existing pipe or tube bundle helical turns around the longitudinal axis, so that a double, triple or multiple helical balancing pre-tur is present. tfζ ^~ I n such a pipe or tube bundle has the ein¬ zelne tube or single tube a helical structure. When the bundle is constructed with seven tubes or hoses, the inner tube or hose is of course ideally not helically wound. Nevertheless, the inner tube or hose can also be designed with a less helical turn than the outer tubes or hoses of the bundle and can preferably be smaller in diameter. rThe distances between the pipes are regulated by the spacers, which are attached to the inside of the pipe or (0 hose).

If two pipes or hoses are twisted around each other ("twisted"), we speak of a double helix-like structure and accordingly for three pipes or hoses of a triple-helix-like structure.

20th

The helical winding of the pipes or hoses over a specific length is 1 m (one

2S meter) preferably 20 to 360 degrees (two to three zero). The helical winding of the tubes or hoses of a tube or tube bundle can be left-handed or right-handed. The diameter of the pipes or hoses is

* £ ^~ knife preferably according to the capacity of the device ten to fünf¬ tens of millimeters. The wall thickness of the heat transfer walls, ie the tube or hose walls, is preferred

HO

0.4 - 1 mm (zero point four to one millimeter). The pipes or conduits may be made of plastic or metal ^ Y ^"or other material. The other parts of the heat exchanger according to the invention may consist of metal, cloth Kunst¬ or consist of ceramic or other material.

SV

The individual tubes or hoses of a tube or hose bundle have spacers at regular, longitudinal intervals _ι 5 $ ^~ , which can be rod-shaped or annular and keep the tubes or hoses laterally at a distance. In the case of flexible hose material, the lateral spacing can also be produced by circumferential bulges which are produced by pressing during heat treatment.

The preferred spacing of the tubes or hoses of a bundle or of the bundles from one another is four to thirty millimeters, depending on the capacity of the heat exchanger.

Short inset to define the language usage:

20th

- If a fluid is guided inside the tube or hose bundle, then we speak of the internally guided one

2iT fluid,

- If a fluid is guided outside the tube or hose bundle, then we speak of the externally guided fluid.

Not every pipe or hose has to carry spacers, but always only one or one directly adjacent pipes or hoses.

Y ^} So if the spacers sparingly over the pipe or

If the hose bundle is distributed, the built-up fluid resistance with this construction minimizes the pressure loss. This is because the desired, optimal turbulence in the external fluid is present anyway (see below). A ζ ^~ 0 too much of a good thing, so too much turbulence leads to

Pressure loss and thus a reduction in the energy saving effect because then for the transport of the fluid

Additional electrical energy must be plugged into the system. 5 If the helically coiled tube or hose bundles are made of less flexible material such as metal or hard plastic, the spacers can be used even more economically or

10 should be omitted entirely, because in such cases the course of the helically wound metal or plastic tube is given by (S the final attachment or stabilizing deflections. Because of the tortuous, helical structure, the raw

10 re a great elasticity and expandability to absorb the thermal change in length, which is particularly the case

2J ^ ^~ application can be observed in boilers. The elasticity of the heat exchanger is of course even greater if the heat exchanger tube bundles have deflections. These deflections are preferably 90 degrees or 180 degrees. The tube or hose bundles can also be deflected.

'lζ ^~ ren by individually these bundles are each wound itself again helically. We then speak of a solenoid, superhelix-like structure. It can even

HO reere tube or preferably tube bundles are helically wound around each other, which we then as double, triple,

^ ζ ~ Multiple super helix.

Especially with a multiple superhelix of the tube or hose bundle for use e.g. for gas-gas heat exchange, a maximum penetration of the two separate fluid flow spaces, namely that of the external

£ 5 ^" and that of the internally guided (def. See above), also for the devices of larger capacity, which are supposed to convert large fluid volumes. 5 ^"

At this point we can make a comparison with the elastic double helix of DNA, whose elasticity ήQ increases in the chromosomal structure due to further helical twist to the superhelix, namely by winding up to super-helix made on supporting histone proteins, whereby at the same time the pearl-like sequence of super

Helix areas the optimal compactness of the chromosome

20 is created.

(Inset on the chromosome structure:

The chain of the super helix areas described above is

2b ^" in turn wound into plektonemic super-super-helix loops, of which six are arranged in a circle

Form ^T jO rosette, the latter then arranged in a spiral to give the phenotype of the chromatid, and finally two chromatids form a chromosome.

For a graphic comparison: if the telephone handset cable represented the chromatid (one of the two strand-shaped chromosome sub-units), the spiral of the telephone handset cable would correspond to the chromatid spiral, the largest subunit of which would be the rosette of the six super-super-helix -Grind

Hrist. )

The elasticity gives the DNA double helix, whose failure can have $ ^~ Q lethal consequences, mechanical protection and simultaneously a mecha¬ cally stable through the helical winding, created optimally compact transport form, which for Zei 1Vermehrung in growth and for Zelltei ¬ elemntar is important in the reproductive process. - ^β r

r Bionically, in the invention "invention M" presented in this patent application, we can not only draw the parallel IQ to the heat exchanger system in the gull feet, but also from a mechanical point of view to the chromosomal helix structure of the DNA.

/ S ^"

The helical deformation of the pipes or hoses, which consist of hard material at room temperature, occurs at

20th

Hard plastic or in the case of metal, for example steel, in the endless process by lateral, mechanical displacement of the drawn, ηjζ ^" pipe passing under heat treatment.

Depending on the material thickness, heat treatment during helical deformation can also be omitted for plastic, cold-deformable steel.

If finite pipe sections are processed, the helical structure can also be produced by a tool-like winding around a solid rod.

HO

For heat exchangers with special applications for pipe production, certain materials, ie metals and Uζ ^~ plastics, are processed in the injection molding process so that the helical structure formed in nascendi with the pipe.

ZurO For optimum turbulence of the internally guided fluid, the individual tubes or hoses can be offset or rounded (by the latter in accordance with "Invention L") by round-necked or pointed-edged indentations or beads. For the object according to the invention, a tube or hose bundle as described above is installed in a cuboid box or a hollow cylinder, which consist of metal, plastic or ceramic, in such a way that the tubes or the Hoses of the tube or hose bundle at the bores of the two end faces of the guaderiform box or of the hollow cylinder are gas or water pressure tight

20 are welded, soldered, screwed or screwed with seal, glued or fastened in any other way.

25 ~ The tube or hose bundle are made from one

D i s t r i b u t i o n s chamber fed with fluid, which flows out of these bundles into a S a m m e 1 chamber, the latter in turn its content in a downstream bundle of the type described or in an outlet

^' ZC, pipe socket released.

The simplest version of the heat exchanger LlQ according to the invention has a simple tube or hose bundle without deflection, an externally guided fluid flow space with a housing, a distribution chamber and a collecting chamber and the associated pipe socket.

In the expanded form, the tube or hose bundle and the externally guided fluid flow space each have at least one, and preferably a 180-degree deflection.

The deflection of the tube or hose bundle can also be realized with the aid of a deflection chamber. _<$ Is brought to the heat exchanger in a gas-gas recuperator for An¬ application, then the pipe or tube bundle within the device to be mounted to extend vertically with an overhead pipe or hose deflection, so that condensates or Druckspülflüssigkeit downwardly from the tubes respectively.

/ r can drain the hoses.

If the heat exchanger according to the invention is used in a boiler, the latter is preferably designed so that

20 the tube bundle run in the vertical direction.

Above this vertical helical tube bundle

2S ^~, instead of a fluid distribution chamber has a wasserge¬ cooled combustion chamber for the use of forced draft burners or Matrixhalbkugel- or matrix rod burner be constructed. Such a combustion chamber, which corresponds to the prior art, can also be deflected, preferably one of 45 or

3S ^" 90 degrees to the shell-and-tube heat exchanger section. In another boiler design is located below

HO of the tube bundle described instead of the fluid flow chamber (distribution, collection) a combustion chamber equipped with an atmospheric gas burner £ f £ ^" .

In the heat exchanger according to the invention, the box-shaped, but preferably hollow-cylindrical heat exchanger housing is constructed in such a way that the housing encloses the tube or tube bundle or tube bundle as closely as possible, preferably only with a spacing of five to ^> fifteen millimeters, so that even in the inner peripheral area of the heat exchanger unit there is optimal turbulence. In terms of flow technology, the internally guided fluid mass flow, i.e. also its core flow, is divided into several smaller ones, from one to the next until it is reached

AO flow chamber (collection, deflection) separate fluid sub-streams divided, and secondly the internal fluid flows

4 $ ^{~ of} a partial flow through the pipes or hoses and is continuously deflected by the bending of the helical twist, which permanently creates turbulence in the internal fluid, which ensures good heat transfer. Additional turbulence occurs when the pipe or

2 $ T hose bundle deflections e.g. 180 degrees.

If the heat capacity of the externally guided fluid is sufficient and the flow velocities of the fluids are set accordingly, then even greater turbulence can occur in the internally guided fluid due to the above-described ones

J $ ^~ professionalizations of the pipes or hoses are generated.

Is in a heat exchanger device according to the invention a tube or hose bundle or a group of tube or

Ho tube bundles at least downstream of a second bundle and a second group of bundles of this type, then lf ^~ $ inside the guided fluid is mixed in the intermediate deflection chamber. If heat exchangers according to the invention are designed with bundle deflections sro, or if they are equipped with deflection chambers, then in the case of the spatially optimal Ξeven bundles So, helical deformation and also a smaller diameter and centrally located tube or hose can be dispensed with. Turbulence and even core flow turbulence are also generated in the externally guided fluid because the bundle of helical tubes or hoses penetrates and divides the externally guided flow space and thus the externally guided core flow space. The helical winding of the outer surface of the pipes or hoses means that the surface on which the

Particles of the external fluid continuously hit

2.0 shifted and thus generate permanently by the impact and the deflection of the fluid particles and additionally by the

Fluid mass displacement of the pipes or hoses in them

2S ^" external fluid flow space spatially extensive turbulence.

2) 0 As a result, the externally guided core flow, which is mechanically divided into partial flows, i.e. its dynamic and c o n t i n u i e r l i c h short-term arising, reuniting and newly emerging t e i l s t r oms due to the turbulence generated here

UQ permanently swirled and mixed.

Local, heterogeneous temperature layers resulting from heat transfer are homogenized after a short time. This ensures an optimal heat transfer from or to the outside fluid.

The heat exchanger according to the invention is preferably operated under counterflow of the fluids. The tube-like or tube-like deflection is preferably used in gas-gas heat exchangers, for example in room air heat recovery devices or malt, wood or paint drying heat recovery devices. 5 ^"

If a redirection is required for an application in a boiler for reasons of capacity or due to compactness and minimized size, then such a boiler is preferably equipped with a deflection chamber. A special feature of the heat exchanger presented in use under countercurrent as a room air heat recovery device is that the heat exchanger according to the invention provides such

L.0 a device can be compressed to a volume of approx. 0.3 cubic meters with a throughput of thousands of cubic meters of air / h.

When using the heat exchanger presented in a natural gas-fed low-temperature boiler, the heat

^ O 1ieferfluid, the heating gas, in the primary heat exchanger inside the tube bundle and the heat transfer fluid, the water, led outside the tube bundle. In the case of hot water

35 ^" boiler technology is also used for a natural gas or biogas-fed boiler, but for the associated U @ secondary heat exchanger, the heating gas is conducted outside the hoses and the burner fresh air inside the hoses.

H £

When used in an air heater, several short tube bundles are staggered side by side and one behind the other, O hot heat supply fluid is routed inside and with the help of a fan installed on the side, large volumes of air can be forced through the tube bundle in cross flow. The advantage is that such a device comes without slats, which is advantageous in terms of cleaning. 5 ^"

The good cleaning and maintenance option is another special and outstanding feature of the heat exchanger presented in.

Is used, for example, when used as a room air heat recovery device, - as a recuperator with separate fluid flow spaces and optimal heat recovery with 100%, that is, complete replacement of the exhaust air with 2 _. 0 Fresh air - the clean fresh air routed inside and the exhaust air loaded with dirty cargo outside, i.e. outside the hose bundle, then settles over time

2b ^"

Dirt on the tube bundles, e.g. can be easily cleaned with a steam jet because the housing of the heat

3 _> 0 exchangers can have at least one side, removable flap or wall. The contaminated parts are therefore convenient and easily accessible for cleaning maintenance. This good, practical property of the device is important for use in kitchens, restaurants, gas facilities, cattle

UQ stall and many other commercial and industrial areas.

(/ ^ ^~ A particularly contemporary and all the more future-oriented application of the heat exchanger according to the invention, preferably in the simple form without deflection, is the use as an o compact, space-saving, practical waste water heat recovery device which is used for the initial equipment of buildings but it is also practical and quick to install without retrofitting. ^" Because of the ever better insulating window glazing and the opaque thermal insulation systematically carried out by the population in building constructions that are conventional, so that

10 both heat insulations taken together can even result in negative K values, the heat recovery from | 5 ^"of the generated wastewater is of greater importance. This is particularly true for the integration into the home automation technology of low-energy houses lo

The installation is particularly interesting in the case where the building services are electrical with photovoltaically generated electricity

2S ^{~ is} supplied so that the feed pumps are also driven in this way.

For this purpose, the heat exchanger according to the invention is integrated into the building services system in such a way that the cold fresh water feeding the boiler or that belonging to the heating circuit system

7.5 ^" cold return water flowing back to the mixing valve or to the boiler or wall heater within the bundle or

Group of bundles of helical tubes or hoses

HD will.

In the outside guide room, the house wastewater from Du- Lj.ζ ^~ see, bath, sink, dishwasher, washing machine etc. is routed in countercurrent, which often has elevated temperatures when leaving the house without a heat recovery system.

SO

Such a waste water heat recovery device can even be installed on waste water pipes, whereby we can speak of "waste water flow cooler (AW-DLK)" in ^" 5 ~ based on the conventional name" fresh water flow heater ". If the toilet faecal wastewater is not separated from the other domestic wastewater by pipeline, the AW-DLK-System IC can be installed technically so that when the toilet flush is triggered, it is controlled by an electrical or electronic signal on the downpipe, where the branch to the AW-DLK located with

IS ^" mechanical, hydraulic or pneumatic support a bypass flap is flipped, which then without detour

20 direct way into the downpipe.

On such an AW-DLK device there is a cleaning flap on the side and watertight so that the external fluid flow space can be easily cleaned. Of course, a pressurized flushing-cleaning system fed with fresh or rain water can also be installed, which is switched on automatically or automatically if the temperature differences are unsatisfactory.

The invention is illustrated by way of example in the drawings and is explained below with reference to the drawings in

HO explained. Show it:

1 is a schematic, lateral, vertically drawn U-Längs ^~ longitudinal section through a gas-gas recuperator,

2 shows a schematic view of a tube or hose bundle with a schematic cross-section at the end, o

3 shows two schematic longitudinal sections through short sections of a tube or hose bundle, FIG. 4 shows a schematic longitudinal section of a short section of another embodiment of a tube or hose bundle according to the invention. Show it :

5 shows a schematic cross section through a tube or hose bundle according to the invention, FIG. 6 shows a detail from FIG. 1 in a schematic longitudinal section, FIG.

7 shows three schematic, different, horizontally drawn longitudinal sections of the gas-gas recuperator already shown in FIG. 1, FIG. 8 the schematic, perspective view of a simple basic version of the heat exchanger according to the invention,

9 shows a schematic, laterally and vertically drawn longitudinal section through a heating boiler according to the invention,

Fig.10 is a schematic, vertically drawn

Longitudinal section through a wastewater flow cooler,

$ 3 ^~

11 shows a schematic, vertically drawn

Longitudinal section through a wastewater flow cooler, Lfö which is connected via a bypass flap branch and second branch to a wastewater line and Fig.12 in Fig.12a and Fig.12b a wastewater pipe branch with a new, integrated bypass flap.

The in Fig.l in Appendix 1/9

The gas-gas recuperator shown in this way has two heat exchanger lower units B and C, which have the partition 20 in common ζY ^~ and are connected to one another by the deflection chamber 50b. A subunit - we now consider B in more detail - is composed of the fluid flow space 18, the fluid flow space 10b, the distribution chamber 50a, the left half of the deflection chamber 50b, the left half of the housing 2, which is in the fluid flow space 18 inner fluid (S guide wall 21b and the pipe socket 4 and 6. The complete fluid flow space 10b from B is composed of the inner space of the pipe or hose bundle 10a (here 0

Hose bundle) and the interior of the Distributons chamber and the left half of the deflection chamber. $ ~ Both fluid flow spaces, 18 and 10b, are structurally arranged in the vertical direction.

In the upper area of subunit B, fluid flow space 18 is deflected by 180 degrees. The fluid flow space 10b likewise undergoes a deflection by 180 degrees through a bending of the tube bundle 10a corresponding to C.

In terms of flow, the gaseous heat supply fluid Y, here warm or hot air (exhaust air), flows through the O.

Pipe stub 6 in the distribution chamber 50a and passes from here through the forierte provided with bores, specifically per- S ^~ partition wall 40a in the tube bundle 10a of the fluid flow chamber 10b. In countercurrent to Y, the heat transport fluid X, o here cold air (fresh air), flows in the fluid flow space 18. The fluid Y, on its way through the helically wound hoses of the hose bundle 10a, emits its heat to the hose walls, from where the heat passes to the counter-flowing fluid X. h The path of the fluid Y first leads upwards through the tube bundle 10a, then downward via the 180-degree tube deflection in the opposite direction into the deflection chamber 50b, which extends between the two end walls 21a and 22a of this chamber, here again ascending / ζ ^~ quietly the fluid passes into the fluid flow Y space 10b of the sub-unit C, which is also made of tube bundles 10a. After another hose deflection in the upper area

10 of subunit C, the now cooled fluid Y arrives in the collecting chamber 50c, from where the fluid Y via the pipe

2 ^ ^" nozzle 7 leaves the device.

The fluid X, which is heated as shown in FIG. 1 during its ^" 2.0 path through the recuperator, begins its path at the pipe socket, 3, then flows through the fluid flow space 19, experiences in the upper region of subunit C that

_2> S ^~ housing 2, the fluid guide wall 22b and the partition wall 20 predetermined 180 degree deflection, switches over the opening 20a L (.Q in the subunit B over and comes in Fluidströmungs¬ space after a further 180-degree deflection finally to Outlet opening, the pipe socket 4.

On the bottom wall 2a, which delimits the chambers 50a, 50b and 50c downwards, and on the intermediate wall 40a there are siphons

£ 0 professionally installed, so that condensates can flow out of the chambers 50a, 50b and 50c and from the compartments of the fluid flow chambers 18 and 19 from above the intermediate wall 40a. These siphons are state of the art and are not shown in FIG. 1. 5 ~ Three sectional planes are marked in Fig. 1, which are shown in Fig. 7.

\ Q Fig.2 in Appendix 2/9 shows the schematic view of a tube or hose bundle 10a, which consists of seven tubes or hoses, the peripheral, six tubes H (10) or hoses H (10) helical convoluted. The front of this

2θ schematic view shows a cross section of this bundle 10a, wherein the central spacer ring 30 can be seen. Within the ring 30, the S central tube or hose, marked H, is shown in cross section.

30

Fig. 3 in Appendix 2/9 clarifies once again the position and function of the T, S stand ring 30 on or between the tubes H or

Hoses H.

Vθ Fig. 4 in Appendix 2/9 shows a different way of spacing, which is preferably used for plastic tubes or hoses. The all-round bulge 30 a is produced by upsetting the pipes H or hoses H with heat treatment. O

Figure 5 in Appendix 3/9 once again shows the cross section of a pipe or hose S ^"bündeis 10a with seven tubes or hoses, with the periph- eral H (10) H and the central and with the centrally posi¬ tioned spacer ring 30. FIG. 6 in Appendix 3/9 shows a detail from FIG. 1, namely a possibility [Q of fastening soft and flexible PE hoses H, the ends 39 of which are drawn out in a ring shape, which abut the perforated intermediate wall 40a and are sealed there can be pressed on by screwing on the perforated counterplate 40b at the level of the dashed lines. In addition, 2θ between 39 and 40a can be sealed with adhesive.

Fig. 7 in Appendix 4/9

^* 2 $ ~ shows the three horizontal longitudinal sections as marked in Fig.l. The seven hoses H of a hose bundle 10a can be seen in section a and section b. The number of five tube bundles 10a, which form part of the fluid flow space 10b, is only exemplary. Definitely

7ς ^~ a number of six or seven bundles of tubes 10a for the fluid flow space 10b is better for the optimal use of space of the fluid flow space 18/19.

Ho

Fig. 8 in Appendix 5/9 shows the simple design 1 of the heat exchanger according to the invention with the markings of the flow directions of the fluids X and Y. The deflection-free heat shown here £ T ^< - ^? Exchanger has a tube or tube bundle 10a, which is formed by the six peripheral, helically wound tubes H (10) or tubes H (10) and the central tube H or tube H. The pipes or hoses are kept at a distance by rings such as 30. 5 ^"

In this simple heat exchanger according to the invention, the tubular or tubular fluid guide space, previously referred to as IQ at 10b, is identical to the inner flow space of the tube or hose bundle 10a. Within the side walls of housing 2 and around the pipes or

/ s-

Hoses H of the bundle 10a extend around the opposite fluid flow space 18, which at the two end faces

2θ sides is limited in the longitudinal direction by the partitions 40a. The partition walls 40a are not permeable to the fluid X but are permeable to the fluid Y because of the bores where the pipes or hoses H are attached. This simple heat exchanger according to the invention also

7) 0 adds a fluid distribution chamber 50a and a fluid chamber 50c for the fluid flow space of Y, which extends over the pipe socket 6, the distribution chamber 50a, the bundle 10a, the collecting chamber 50c and the pipe socket 7. The fluid flow space 18 for the fluid X has

Vθ also via connection pipe socket, namely a return pipe socket 3 and a flow pipe socket 4.

^^ ^"The marked A region which extends over the nipple 6 and the distribution chamber 50a may be replaced by a water-cooled combustion chamber which at any angle but preferably at a 90 degree angle is applied. In such a case, is the invention Warmth-

£ ^"S ^~ to stand exchanger in the boiler construction in vertical overhead combustion chamber. A specific Brenn¬ chamber can be equipped with matrix or blower burner. S ^~

Area A can also be replaced by a water-cooled combustion chamber located at the bottom, in which case the IQ operation of a dynamically driven, atmospheric burner is recommended.

If such a simple heat exchanger according to the invention as shown in FIG. 8 is used as a gas-gas recuperator, then it is also possible to use a super-thermal winding of, for example, flexible PE hoses. To such a heat exchanger gewun with superhelical ^¬ which introduce hoses pictorially, is labeled (10) in place of the s- H, helical coiled tube intended a consisting of at least two hoses tube bundle 10a, 3C, in which case the Guppe 10b of the tube bundle 10a superhelical wound is, and so a superhelix tube structure 10c is formed.

Fig. 9 in Appendix 6/9 shows schematically the structural arrangement of the boiler

Ho components in a boiler that has the heat exchanger according to the invention. The symbol for the tube bundle 10a fζ ^~ indicates that in this boiler Wärmetau¬ the shear may be provided with a tube bundle erfindnungsgemäßen 10a or 10b with a group of tube bundles 10a. O

9, the newly emerging names are briefly mentioned: the boiler shown with the heat exchanger according to the invention has the combustion chamber 8, the water-carrying combustion chamber jacket space 9, the combustion chamber opening 8a, the brackets 11 and the siphon 12. S ^"Fig.10 shows a 7/9 in Appendix, deflection-free according to the invention, under Gegen¬ current working heat exchanger, which in the Abwasserlei-

10 tung 13 of a house is integrated.

The heat exchanger according to the invention here fulfills the function 1b of a heat recovery device, specifically when used as a "wastewater flow cooler".

20th

Fig.11 in Annex 8/9 shows the heat exchanger according to the invention in the same _ζ ^~ function as in Fig. 7. However, this time the device according to the invention is integrated in a waste water down pipe 13, which also transports coarse particles at times.

3o

For this reason, the pipe branch 13a is equipped with a simple, circular, bypass flap 15 which is moved 7, C, mechanically, hydraulically or pneumatically via the rod 15a. Laterally, the construction shown is that of the invention

Ho device equipped with a cleaning flap 17 sealed by cord seal 16.

12a and 12b in appendix 9/9 show a single-hinged slide device, which also

$ v is to be opened if a signal malfunction should have led to a blockage of the side branch 23a 5 ^{~ "} £ ^~ or the pipe socket 3 and / or the downpipe 13 above the slide flap 25 when the toilet flush was triggered. b

It is advisable to install a screen filter on the side branch pipe 23a between such a bypass flap device as shown in FIG. 12 or in FIG. 11 and the pipe socket 3 of the heat exchanger according to the invention. S The sieve can preferably be cleaned automatically, i.e. without opening a cleaning flap, with the

Pressure flushing of the screen water arising line via a muffenschieberkontrol 0 1 ierten branch to the side branch pipe 23a to the bypass section 13b of the drain Abwasserfal 13 S ^~ can.

The flap 25 is oval in shape, so that despite the oblique positioning of the flap 25 in FIG. 12a, the side tube 23a and in FIG. 12b, the downpipe 13 is well sealed. The explanations of the other reference symbols and further _ _> ^" explanations can be found in the reference symbol list.

fT

0 W E R M E T A U S C H E R

| <T B E Z U G S Z E I C H E N L I S T E

A ΞCollecting chamber with pipe socket {) B left subunit of recuperator in Fig.l

C right "" "" "" 1

H pipe or hose

2 ^ X fluid (here: heat transfer fluid)

Y fluid (here: heat1 supply fluid)

}, 0 1 heat exchanger according to the invention, deflection-free, as shown in Fig.8

2 housing 2a bottom wall

3 pipe sockets (here: return) fO 4 "(here: flow)

6 7

HS-

8 combustion chamber

8a combustion chamber opening ro 9 water-bearing combustion chamber jacket

10 helical tube or hose

10a tube or hose bundle

10b middle part of the fluid flow space of Y, in FIG. 1: group of tube or hose bundles 10a 5 10c superhel ix-like winding of a group 10b of tube or hose bundles 10a 11 console

1 '° 12 siphon

13 sewage pipe / 5 ^~ 13a pipe branch

13b bypass section of the sewage pipe

15 bypass flap, circular

10

15a rod

15b electromechanical, hydraulic or

25 "pneumatic unit

16 cord seal

17 cleaning flap

18 Fluid flow space for Fluid X

19 """" XT, ς ^~ 20 partition

20a opening in the lower region of the partition 20 21a end wall of the deflection chamber 50b

Release

22a "" 50b

21b fluid guide wall ^ 22b

23a side branch pipe 23b side branch pipe see above

24 sleeve seal

25 oval flat sliding flap ζζ ^~ 25a half-closed flap 25

26 inside the pipe branch on both sides opposite groove, serves as a guide groove of the pin 28th 27 eyelet suspension

28 pins projecting laterally on both sides of the oval flap 25 0

29 lower limit of the groove, serves as a slide rail S ^{~ of} the pin 28

30 spacer ring

30a circumferential bulge 0

39 ends of the hoses H 40a drawn out in a ring-shaped manner with an intermediate wall S "40b" "" "" counterplate

50a distribution chamber 50b deflection chamber 50c collecting chamber

T

Claims

S ^"

10

W E R M E T A U S C H E R lb

P A T E N T A N S P R Ü C H E

10th

1.

2_g ^~ Device for heating a heat transport fluid, in which the heat transport fluid and a heat supply fluid have a heat exchanger with fluid flows separated for the two fluids.

Flow through 30 mung spaces, so that the one fluid flow space from T, ς- the interior of at least one tube or hose bundle and the interior of two tube or hose bundle ends, through holes fluid-tight and fluid flow through-

40 casually connected and each with at least one

Pipe connection equipped, box- or hollow-Lf.ζ ^~ derförmigen flow chambers is formed, wherein the Rohr¬ or tube bundle consists surfaces of at least two pipes or Schläu¬ and about the longitudinal axis helically twisted o ~ 0

Has a structure that arises from the fact that each individual tube or hose has a helical right- or left-turning structure, and .... (Contd. On page 30) -> to l. : ...., and (continued from page 30) the other fluid flow space is formed from the space which is inside a box-shaped or hollow cylindrical, 0 surrounding the tube or hose bundle but outside of this or this tube or hose bundle fS del is located, the two end walls of this housing being fluid-impermeable but with the bore-bearing walls of the adjacent tube or hose bundle end

20

Flow chambers, which belong to the first-mentioned fluid flow space, are identical and therefore for both fluid

25T flow spaces represent common partitions, and this housing of the second-mentioned fluid flow space is equipped with at least two pipe connecting pieces.

Second

Apparatus according to claim 1, d a d u r c h g e k e n n- ^ z e i c h n e t that the tubular or tubular part of the heat exchanger is not from a tube or hose bundle

T or formed by tube or hose bundles, but by one or two or more, individually positioned, helically structured and, if in multiplicity, grouped but not wound around one another or not twisted together, likewise do not occur in bundles - the tubes or Tubing is formed.

S Device according to claim 1, 2 or 4 thereby - indicates that the heat exchanger is operated under counter-current and / or cross-flow of the fluids. 4th ST

Device according to claim 1, dadurchgekenn ^¬ characterized in that the röhr- or tubular part is formed (Q of the heat exchanger at least one tube or Schlauch¬ bundle which a central and six peripheral helical balancing pre-tured pipes or hoses, helical

IS has a structured or non-helically structured pipe or hose. 20 5.

Device according to one of claims 1 to 4, d a d u r c h g e k e n n z e i c h n e t that the tube or hose

2S ~ -shaped part of the heat exchanger is bent over once or several times in the main direction, that is to say has at least one deflection 2P. 6.

Device according to claim 5, dadurchgekenn - characterized in that the bend or bends as a 180-degree deflection or as a 180 degree deflections bt out ^¬? forms is or are.

7. ^ b device according to one of claims 1 to 4, characterized in that the one fluid leading de, tubular or tubular part of the heat exchanger is bent one or more times, and also the tubular or tubular Part and the housing part of the heat exchanger which surrounds the other fluid flow chamber and is designed or are designed with a corresponding deflection or with corresponding deflections. r β.

Apparatus according to claim 7, characterized in that the bend or bends lo of the tubular or tubular heat exchanger part and accordingly the deflection or the deflections of the housing part of the heat exchanger carrying the other S fluid with 45 degrees, 90 degrees or Is or are 180 degrees.

Device according to one of claims 5 to 8, so that the tubes or hoses are not helically structured in the region of the tubular or tubular deflection or deflections.

30

10th

Device according to one of claims 5 to 9, characterized in that at least one bend of the tubular or tubular part of the heat exchanger is designed as a deflection chamber, the fastening of the tubes or hoses to the deflection chamber being made in the manner as is specified in claim 1 for the attachment of the tubes or hoses to the bores of the flow chamber walls. O

11th

The apparatus of claim 10, dadurchgekenn - S ^~ characterized in that the deflection chamber or the deflection chambers in each case a deflection or diversion of 45, 90 or 180 degrees is constructed or are. S ^~ 12.

Device according to one of claims 1 to 11, d a d u r c h g e k e n n z e i c h n e t that at least one pipe or

! C at least one tube of the tubular or tubular part of the heat exchanger is staggered by round-necked or pointed-edged indentations or beads or is otherwise profi

10

13th

Device according to one of claims 1 to 12, characterized 2 & ^~ 9 ek that at least one tube or hose of a group of nearest neighbors of tubes or hoses is equipped with ring, bead, rod or angular or other spacers.

Device according to one of claims 1 to 13, d a d u r c h g e k e n n z e i c h n e t that the heat exchanger from yo

Metal and / or plastic and / or ceramic is made.

Device according to one of claims 1 and 3 to 14, since ¬ characterized in that the tubular-O or tubular part of the heat exchanger from at least one from a tube or hose bundle wound, sole- ζb nooid, superhel ix-like bundle or from one there is at least two coiled, superhelix-like bundle structure. 6 16.

Device according to one of claims 1 to 15, characterized in that for use as a boiler for heating a fluid such as oil or water, as a wall heater or fresh water heater, one of the two final flow chambers of the heat exchanger according to the invention is replaced by a fluid-cooled combustion chamber, the combustion chamber at any angle, but preferably with

20th

45, 90 or 100 degrees constructionally attached to the heat exchanger and depending on the selected burner technology 2S ^~ related to the longitudinal axis (0 - / 180-degree axis) of the tubular or tubular part of the heat exchanger connected to the combustion chamber and with vertical orientation the same

3o half of the heat exchanger or positioned below the heat exchanger.

3 ^

17th

Device according to one of claims 1 to 15, d a d u r c h

Ho in that a fluid-cooled Brenn¬ is chamber side, fluid pervious connected in any ψ> ^~ angle at the middle housing portion, the combustion chamber surrounding fluid flow space is fluid pervious and hydraulically connected to the fluid flow space, the order from the housing part of the heat exchanger according to the invention ¬ is given and lies outside the other fluid flow space ζS, which extends within the tubular or tubular heat exchanger part and the flow chambers terminating thereon. _ 18. 0

Device according to one of claims 1 to 17 d a d u r c h g e k e n n z e i c h n e t that the heat exchanger with

| Ö at least one cleaning door or flap is fitted.

19. (b device according to one of claims 1 to 15 and 18 d a-d u r c h characterized in that via the connecting pipe socket of the heat exchanger part, the fluid flow space outside

20 of that of the tubular or tubular heat exchanger part, the heat exchanger is fluid-lb permeably inserted into a sewage line and the connecting pipe sockets belonging to the tubular or tubular heat exchanger part are connected to a heat-consuming system such as e.g. the room heating system or the fresh water heating system is connected.

20th

The apparatus of claim 19, ¬ dadurchgekenn characterized in that the heat exchanger is connected on the side of the TFQ sewage line via pipe branches, the pipe branches are connected via the sewage pipe bypass section, and in abwasserzuführenden pipe branch an elec- tro-mechnaisch, manually, hydraulically or pneumatically betae ^¬ bypass valve, and between this pipe 1? branching and the connecting pipe stub flow of the heat exchanger is a screen filter, which is preferably automatically tr ^<~ is to be cleaned and a private branch pipe MUF fenschieberkontrol 1 the resulting Druckspülreiaigungs- ated water in the bypass section of the sewer pipe discharges. S- 21.

Apparatus according to claim 20, d a d u r c h g e k e n n ¬ z e i c h n e t that the bypass valve, which is in the

} 0

There is a heat exchanger towards the waste water supply pipe branch, which is a single-flap bypass flap which has an oval shape and is attached to a pointed end directed towards the branch opening via an eyelet on a slide rod, and two opposite, laterally protruding

20

Carries pins which are guided when the flap is actuated by two grooves embedded in the side of the pipe branch, and

2S ~ which is bent slightly upwards at the end opposite the eyelet in the direction of the rod side.

30

22.

Device according to one of claims 19 to 21, so that the connection pipe socket of the heat exchanger that leads back to the sewage pipe is smaller in tjQ diameter than the diameter of the connection pipe socket that leads from the sewage pipe to the heat exchanger.