WO2006032258A1

WO2006032258A1 - Heat exchanger

Info

Publication number: WO2006032258A1
Application number: PCT/DE2005/001675
Authority: WO
Inventors: Josef Bachmaier
Original assignee: Josef Bachmaier
Priority date: 2004-09-23
Filing date: 2005-09-22
Publication date: 2006-03-30
Also published as: EP1800079A1; DE102004046587A1; US20080257534A1; DE102004046587B4; DE112005002917A5; WO2006032258B1

Abstract

The invention relates to a heat exchanger provided with channels (3.1, 3.2) which are separated by separating walls, and which are cross-flown in an alternating manner to the counter flow by one or the other flow mediums (W, K). Said heat exchanger is formed by a spiral-shaped, wound, sheet-like material (1). The windings (2.1, 2.2,...) of the spiral form the separating walls between the channels (3.1, 3.2,...). The channels (3.1, 3.2,...) are also separated from each other by separating webs (4.1, 4.2,...) which are arranged between adjacent windings (2.1, 2.2,...).

Description

heat exchangers

The invention relates to a heat exchanger according to the preamble of claim 1.

Various types of heat exchangers are known, for example tubular heat exchangers, plate heat exchangers, etc. As different as they are in their nature, so are the fields of application. For example, heat exchangers are used for room ventilation, but are also used, for example, in Stirling engines or nitrogen engines. In addition to a high degree of efficiency and low production costs, a small space requirement and a high pressure and / or heat resistance are often required.

The object of the invention is to provide a heat exchanger which meets these requirements.

This is achieved according to the invention with the gekennzeich¬ in claim 1 Neten heat exchanger. In the subclaims advantageous embodiments of the invention are shown.

According to the invention, the heat exchanger is produced in a simple manner in that at least one sheet-shaped material is wound around the longitudinal axis of the heat exchanger. In cross section, a spiral with spaced windings is thus formed. The turns thus form the partitions while the channels are spaced through the space between the ones Turns are formed. In order to separate the individual channels from one another, separating webs can additionally be provided between adjacent turns which extend along the heat exchanger from one end face to the other. Thus, a channel is formed between two turns and two separating webs. As a result, a compact, space-saving construction of the heat exchanger according to the invention is ensured. In addition, the heat exchanger can be pre-produced by the meter with any number of turns and with any desired dimensions.

The channels are alternately flowed through in countercurrent of one or the other flow medium, between which the heat transfer takes place. That is, the innermost or first channel between the innermost or first turn and the second turn is flowed through by the one, for example, warm flow medium in one direction and the second channel between the second turn and the third turn of the other, colder flow medium in the opposite direction ¬ tion, the third channel again from the warm flow medium, etc.

The flow medium can be both a gas and a liquid, but for example also a solid heat storage mass having a melting temperature below the temperature of the warm flow medium, for example paraffin, wax or fat. The sheet-like material may be metal, plastic or another material, as long as it can be wound or produced in a gewi¬ ckelt. In the case of a gaseous flow medium and less extreme requirements, for example when used for room ventilation, the sheet-like material can be plastic. At high temperatures, for example, a stainless steel sheet can be used. In particular, when the partitions from the sheet-shaped Mate¬ material are integrally formed, the heat exchanger according to the invention has a high pressure and temperature resistance. In order to increase the compressive strength, punctiform connection points can be provided between the windings, preferably in the longitudinal direction and around the circumference.

In order to lengthen the flow path with the same length and the same diameter of the heat exchanger and thus increase the degree of efficiency, the individual channels are preferably closed at the end faces of the heat exchanger via a pitch circle and open at the other end face via a pitch circle. If the separating webs run parallel to the pole axis of the spiral, that is to say parallel to the longitudinal axis of the heat exchanger, the closed pitch circle of a channel preferably faces an open pitch circle on one end face on the other end face. Thus, the flow medium does not flow straight through the channels, but is deflected in the circumferential direction, so that it emerges on the other end face, based on the cross section of the heat exchanger, on the gegenüberliegen¬ the side. In other words, if, in the case of a horizontally arranged heat exchanger, it enters the channel at the top or at the right in the channel, it exits at the other end side at the bottom or at the left.

The pitch circles are preferably formed by semicircles. The open pitch circles or semicircles, via which the flow medium enters the heat exchanger, are preferably arranged on the same side or half of one side of the heat exchanger, and the open pitch circles or semicircles over which the other flow medium on the other end face in the opposite direction, on the gegenüberlie ^¬ ing side or half of the other end face. That is, in a horizontally arranged heat exchanger and extending parallel to the longitudinal axis separating webs, the open part or semicircles are hen vorgese¬ example, bottom or right for the entry of a flow medium, and the open part or semicircles on the other end face for the entrance of the other Flow medium in countercurrent top or left. Thus, the connection of the heat exchanger is much easier, because the one Strö¬ tion medium at one end face and the other flow medium in countercurrent on the other end side in each case on one side or half of the respective end side can be connected sen sen.

However, the dividers can also extend helically around the polar axis of the spiral, ie the longitudinal axis of the heat exchanger. The helix angle can be 180 ° or a multiple thereof. Thus, the flow medium can in each case on the same side on the one end face and emerge on the other end face ren, ie. enter at a horizontally arranged heat exchanger in the upper half at one end face and emerge at the upper half from the other end face.

The heat exchanger according to the invention can be used in different fields. For example, it can be used in nitrogen engines in which liquid nitrogen is expanded with air, that is, in which the nitrogen forms the cold flow medium and the air or water countercurrently forms the warm flow medium. Another possibility is the Stirling machine, since the heat exchanger according to the invention is able to withstand a high pressure and high temperature. The heat exchanger according to the invention can furthermore be used as an absorber for heat pumps, furthermore, for example as a water / air heater, eg as pre- or post-heating register. It is also ideal for geo-thermal plants.

If an electrical contact is made on one and the other side of each turn, the heat exchanger according to the invention can also be used to obtain thermo-power according to the Peltier effect.

Below, three embodiments of the heat exchanger according to the invention are explained in more detail by way of example with reference to the accompanying drawings. In each case schematically show:

1 shows a heat exchanger according to a first Ausführungs¬ form in a perspective view;

Figure 2 and 3 is a plan view of the one or the other end face of the heat exchanger;

Figure 4 is a cross-section along the line IV-IV in Figure 1;

Figure 5 shows a cross section through the heat exchanger according to a further embodiment;

Figure 6 and 7 is a plan view of an end face of the

Heat exchanger without or with cover according to Figure 5;

FIG. 8 is a plan view corresponding to FIG. 7, however, of a heat exchanger designed as a mixer;

9 shows a cross section through the heat exchanger according to a third Ausführungsfόrm. and FIG. 10 shows a plan view of an end face of the heat exchanger according to FIG. 9 with the cover for one of the two flow media.

The heat exchanger according to the invention consists of a sheet-like material 1, which is spirally wound around the longitudinal axis of the heat exchanger or polar axis P of the spiral. The turns 2.1, 2.2, 2.3, ..., 2.6 of the spiral form the partitions of the heat exchanger, while the channels 3.1, 3.2, ..., 3.5 are formed by the space between the adjacent turns.

In order to separate the individual channels fluid-flow-tight from each other, additional dividers 4.1, 4.2, ..., 4.5 are provided between adjacent turns 2.1, 2.2, 2.3, ..., extending along the heat exchanger from one end face A to the other end face B.

The channels 3.1, 3.2, ... are alternately flowed through in countercurrent by the warm flow medium W or the cold flow medium K, wherein the warm flow medium W enters at the end face A and exits cooled at the other end B as Wk, while the cold Flow medium K enters at the end face B and exits heated at the end face A as Kw.

That is, the innermost or first channel 3.1 between the inners¬ th or first turn of 2.1 and the second winding 2.2 is of the cold flow medium K in the one direction by ^¬ flows and the second channel 3.2 between the second winding 2.2, and the third turn 2.3 from the warm flow medium W in the opposite direction, the third channel 3.3 again from the cold flow medium K, the fourth channel 3.4 from the warm flow medium W and the fifth channel 3.5 again from the cold flow medium K. In order to extend the flow path and thus increase the efficiency, the individual channels 3.1, 3.2, ... are closed at both ends A and B of the heat exchanger via a semicircle 5.1, 5.2, ..., 5.5 and open therebetween. The closed semicircle 5.1, 5.2, ... on one end face A is an open semicircle 6.1, 6.2, ... on the other end face B opposite. The closed semicircles 5.1, 5.2,... Extend in each case as far as the respective separating web 4.1, 4.2,. Since the separators 4.1, 4.2,... Run parallel to the polar axis P, the flow medium W or K does not flow straight through the channels 3.1, 3.2,..., But is deflected in the circumferential direction, so that it is connected to the other end face B or A exits on the gegenü¬ berliegenden half. That is, the flow medium W occurs on the one, left half of the front side A and on. the opposite, ie the right half of the front side B, as Wk again off, while the other flow medium K enters the left half of the front side B and exits at the right half of the front side A as Kw again, so that there the corresponding accessories and drain lines can be connected.

In order to increase the compressive strength of the heat exchanger, point-shaped connection points 6 'are provided between the turns 2.1, 2.2,..., Distributed in the longitudinal direction and in the circumferential direction, which are produced, for example, by spot welding.

The separating webs 4.1, 4.2,... Between the individual windings 2.1, 2.2 are arranged adjacent to one another on one side of the heat exchanger. The end portion of the inner and the outer longitudinal edge 7 and 8 of the spirally wound material 1 is connected to the adjacent turn 2.2 and 2.5, respectively. In the middle of the heat exchanger, a bypass channel 9 is provided, by means of which, for example, cold air, for example in summer, can be conveyed into the room when the heat exchanger is used for room ventilation.

In order to improve the heat transfer, in the channels 3.1, 3.2, ... also lamellae or similar surfaces enlarging body can be provided.

In the further embodiment of the heat exchanger according to Figures 5 and 6, two, so a pair of blades 10 and 11, which are separated by spacers 14, spirally wound around the longitudinal or Polachse P. The channel 13.1 for the one, e.g. warm flow medium W, is determined by the distance between the two sheets 10 and

11 is formed, and the channel 13.2 for the other, e.g. cold flow medium K, by the distance between the inner sheet 11 of the respective outer turn of the sheet pair 11,

12 and the outer blade 10 of the adjacent inner turn of the pair of blades 10, 11th

In the channels 13.1 and 13.2 (not shown), for example, helical dividers may be provided to extend the flow path. Also, the channels 13.1 and 13.2 may have a different width by spacers 15 of different lengths. For example, in the case of an air / heat exchanger, a wide duct 13.2 for the passage of air and a narrow duct 13.1 for the passage of water can be provided.

In FIG. 5, at the same time, the contacts 15, 16 for the removal of the thermo-current according to the Peltier effect from the sheet 11 are shown, which are heated on one side by the warm flow medium W in the channel 13.1 and on the other side is cooled by the cold flow medium K in the channel 13.2.

The heat exchanger according to the invention can also be designed for three or more media. For example, if a divider is provided in one of the channels 13.1, 13.2 to form three channels, e.g. through a channel, the heat transfer fluid heated by a solar system flow, in the second channel may be provided a heat storage mass, e.g. Paraffin or fat, and through the third channel in the passage e.g. Water flows to get warm water.

According to FIG. 6, also in the embodiment according to FIG. 5, the channel 13.1 can be closed on one end side on one, for example the left side and open on the other side, while the channel 13.2 on this front side is open on the left side and on the right side closed is. By attaching corresponding covers 17, 18 with pipe connections 19, 20 on the respective side of each end face, the corresponding inlets and outlets for the respective flow medium can be connected. With the lid, the bypass channel 6 is closed.

If the bypass channel 6 is connected to the channel 13.1 and / or 13.2, the heat exchanger can also be used as a mixer. As shown in FIG. 8, the cover 18, from which the warmer flow medium emerges, then also extends over the bypass channel 16.

The embodiment according to FIGS. 9 and 10 differs from that according to FIG. 5 essentially in that the two blades 10, 11 of each pair act at a first predetermined angle α and the inner blade 11 turns with the outer blade 10 of the adjacent inner Winding after a second predetermined angle ß, the predetermined to the first Angle α, are interconnected to form the channels 20.1, 20.2, 20.3 for one and 21.1, 21.2 and 21.3 for the other flow medium.

The connections between the leaves 10, 11 of a pair are formed by constrictions 23 of the pairs of leaves.

The angle at which the constrictions 23 are offset relative to the connections 24 between the inner blade 11 of one turn and the outer blade 10 of the respectively adjacent inner turn is .alpha. / 2. In this way, the channels 20.1, 20.2 and 20.3 for the one, for example, cold flow medium K, and the channels 21.1, 21.2, 21.3 for the warm flow medium Wk are each arranged radially one behind the other. Compared to the embodiment of Figure 5, the heat exchange surface is increased in this embodiment.

1

In Figure 10, the lid 26 is shown schematically, the channels 21.1, 21.2, 21.3 closes at one end face of the heat exchanger to connect them with the drain line for the flow medium Wk. The cover 26 has radially extending wings 27 which cover the channels 21.1, 21.2 and 21.3. The gussets 28 at the constrictions 23 and connections 24 are closed in order to separate the two flow media from one another. The cover, not shown, at this end face for connecting the supply line for the cold flow medium K to the heat exchanger 1 is constructed in a manner similar to the cover 26.

In the two embodiments according to Figure 1 to 4 or 5 to 8, the inlet and outlet of the flow media at the two end faces of the heat exchanger 1 also take place in several pitch circles, ie not only in the form of semicircles, as shown in Figure 1 to 4 or 5 to 8. For example, it is possible to have two partial circles each with 90 ° to the entrance and two partial circles each with 90 ° to the exit or six partial circles each with 30 ° to the entrance and six partial circles each with 30 ° to the exit or four partial circles with 60 ° to the entrance and two subcircuits each with 60 ° to the outlet or two subcircles each with 160 ° to the inlet and two subcircuits, each with 20 ° to provide for exit on each end face of the heat exchanger.

Thus, in the case of gases and high temperatures, the inlet and outlet openings can be adapted to the volume changes due to the cooling or heating via the size of the opening angles of the individual partial circles to the inlet and outlet volumes. That is, if a high-temperature gas over a Teilkreis¬ area of e.g. 60% or a total proportion of Teilkreis¬ surfaces of e.g. 60% enters at one end face, the volume decreases as a result of the cooling and occurs at the other end face of the heat exchanger with e.g. 40% of Öff Öff nungsfläche again off. Likewise, for the cold gas, e.g. 40% of the total area for entry at one end and e.g. 60% of the total area to be provided for exit on the other Stirn¬ side of the heat exchanger.

A preferred field of application of this variant of the heat exchanger is the exhaust gas heat recovery, for example in biomass combustion, in which the exhaust gas heats the combustion air.

According to the invention, particularly high-efficiency ventilation heat exchangers can be produced cost-effectively. Here, especially the bypass 6 in the interior is advantageous, especially in conjunction with a mixing valve.

Claims

claims

1. Heat exchanger with separated by partitions channels

(3.1, 3.2, ..., 13.1, 13.2), which are alternately flowed through in the countercurrent of one or the other flow medium (K, W), characterized by at least one spirally wound sheet-shaped material (1, 10, 11) , Wherein the turns (2.1, 2.2, ...) of the spiral the. Form partitions and the channels (3.1, 3.2, ..., 13.1, 13.2, 20.1, 20.2, 20.3, 21.1, 21.2, 21.3) by the Ab¬ states between the individual turns (2.1, 2.2, ...) are formed ,

2. Heat exchanger according to claim 1, characterized in that the channels (3.1, 3.2, ...) by separating webs (4.1, 4.2, ...) between adjacent turns (2.1, 2.2, ...) are separated from each other.

3. Heat exchanger according to claim 1, characterized by at least one pair of spiral-shaped, spaced-apart sheets (10, 11), wherein the channel (13.1) or the channels (20.1, 20.1, 20.3) for the one Strömungsmedi¬ ( W, K) by the distance between the two leaves (10, 11) of the pair and the channel (13.2) or the channels (21.1, 21.2, 21.3) for the other flow medium (K, W) by the distance between the turns of the Blattpaa¬ res (10, 11) is formed.

4. Heat exchanger according to one of the preceding claims, characterized in that the individual channels (3.1, 3.2, ...) at one end face (A, B) of the heat exchanger. About a pitch circle (5.1, 5.2, ...) closed and at the other end face (B, A) over a pitch circle (6.1, 6.2, ...) are open.

5. Heat exchanger according to claim 2, characterized in that the separating webs (4.1, 4.2, ...) parallel to the polar axis (P) of the spiral run.

6. Heat exchanger according to claim 5, characterized in that the closed pitch circle (5.1, 5.2, ...) of a channel (3.1, 3.2, ...) on one end face (A, B) an open pitch circle (6.1, 6.2 , ...) on the other Stirn¬ side (B, A) is opposite.

7. Heat exchanger according to claim 4, characterized in that the closed pitch circles (5.1, 5.2, ...) and the open pitch circles (6.1, 6.2, ...) are formed by a semicircle.

8. Heat exchanger according to claim 2, characterized in that the separating webs (4.1, 4.2, ...) helically around the pole axis (P) of the spiral run.

9. Heat exchanger according to one of the preceding claims, characterized in that the separating webs (4.1, 4.2, ...) adjacent to each other between the turns (2.1, 2.2, ...) are arranged.

10. Heat exchanger according to one of the preceding claims, characterized in that between two turns (2.1, 2.2, ...) in each case a single separating web (4.1, 4.2, ...) is arranged.

11. Heat exchanger according to one of the preceding claims, characterized in that the turns (2.1, 2.2, ...) are point-shaped (6) connected to each other.

12. Heat exchanger according to one of the preceding claims, characterized in that the spirally wound, sheet-like material (1) surrounds a bypass channel (9) in the middle of the heat exchanger.

13. A heat exchanger according to claim 3, characterized in that the two leaves (10, 11) of each pair after a first predetermined angle (α) and the inner sheet (11) of a turn with the outer sheet (10) of the adjacent inner winding to a second predetermined angle (β), which is offset to the first predetermined angle (α), are interconnected to the channels (20.1, 20.2, 20.3) for the one flow medium (K) and the Ka¬ channels (21.1, 21.2 , 21.3) for the other flow medium

(Wk) to form.

14. Heat exchanger according to claim 13, characterized in that the first angle (α) and the second angle (ß) are equal.

15. Heat exchanger according to claim 13 or 14, characterized gekenn¬ characterized in that the angle by which the connections (24) between the inner sheet (11) of a turn with the outer ßer sheet (10) of the respective adjacent inner turn against the Compounds of the two leaves (10, 11) of each pair are offset, which is half of the first angle (α).

16. Heat exchanger according to one of claims 13 to 15, characterized in that the connections between the Blät¬ terpaaren (10, 11) by constrictions (23) of the Blatt¬ couples are formed.

17. Heat exchanger according to one of claims 13 to 16, characterized in that the channels (20.1, 20.2, 20.3) for the one flow medium (K) and the channels (21.1, 21.2, 21.3) for the other flow medium (Wk) to the polar axis (P) are each arranged radially one behind the other.