KR20010013477A - Heat accumulator, especially a pcm device - Google Patents

Abstract

The present invention relates to a regenerator, in particular a latent regenerator, having at least an insulator (4), an inlet (2) outlet (3) and a collecting portion (12) of a heat transfer medium fluidly connected to a regenerator core surrounded by a housing. (Tube) 5 is disposed therein, and the invention device has an interior of a flow path with a phase change material. Such heat accumulators are more easily adaptable to small angle installations, while at the same time retaining storage capacity, high load and no load power characteristics and the flow path 5 is spiral or the flow path 5 is through a corrugated heat storage core. If it is an inverted ellipse or flat tube, it can be manufactured inexpensively, and the part 9 of the phase change material is located between the individual channel 5 and the coil of the waveform 10 or the individual channel 5, and for the most part, the channel 5 Is occupied by a thermally conductive element 8 connected by metal to The thermally conductive elements 8 are made of sheet metal corrugated box trips whose width is larger than the large diameter of the tube forming the flow path 5.

Description

Heat accumulators in particular latent heat accumulators {HEAT ACCUMULATOR, ESPECIALLY A PCM DEVICE}

Such heat accumulators are known in the literature, for example in WO 89/09375. Known heat accumulators have access spaces, in which flow passages (individual flat tubes) flow. Claim set spaces take considerable space, in particular as shown in the figures of the above document.

Problems that have already been mentioned several times that the assembly space provided for the heat accumulator must be small but the heat capacity of the heat accumulator must be the same or rather increased, by improving the storage of lost heat, the need for energy savings is always emphasized and the demands of the industry are increased. do. The contribution to the solution of the present problem for the assembly space of the vehicle has been the regenerator known from DE 195 30 378 C1, but it is never a potential regenerator but a hot water regenerator. As stated in this document, the space is not reduced in volume but is increasingly diverged to make the assembly space so-called complete.

In view of this limitation, the latent heat accumulators known in the original document can no longer be considered suitable for the assembly tubes claimed for their space or also for manufacturing reasons. This structure, for example, always has the necessary relationship between a number of risky solder joints, a large number of components that adversely affect the fabrication process, and the space between the flow path space and the phase change material.

Heat exchangers with a labyrinth flow path (DE 29 42 147 A1) have already been proposed. Such heat exchangers are actually incapable of accumulating, but due to the fact that the phase change material is accommodated in the form of a shell, it is inadequate due to the high manufacturing cost and performance defects. The flow path consists of two flat plates which are joined together, and the flow path is formed by a blower therebetween. The plates between the channels reduce the space of the phase change material, thereby reducing the heat storage capacity.

The latent heat accumulators of DE 32 27 322 A1 consist of modules stacked on top of each other and surrounded by insulation. In a separate module surrounded by the housing, a spiral hollow body connected at the center is disposed. The space is taken into account in the housing, in which the latent heat storage means is capable of expansion upon melting. The latent heat accumulator consists of a heat accumulator tank to be installed in a building, in which a heat accumulator having a large load and no load power is provided in a narrow space, and the latent heat accumulator medium should be completely melted as much as possible. The complex perfusion and control of the heat transfer medium are taken into account.

The present invention relates to a latent heat accumulator having at least one entry and exit space for a heat accumulator, in particular a heat accumulator, which is in fluid connection with a heat accumulator, in particular a heat insulator, a heat accumulator core enclosed by a housing. There are spaces in it, and there is a phase deformation material.

1 is a perspective view of a latent heat storage device; Front open

Fig. 2 Principle of a heat storage body whose cross section is a formulation

Figure 3 Alternatives

Fig. 4 Main Heat Storage

5 perspective view

Fig. 6 Built-in tube accumulator

7 and 8 Examples of the principle of heat storage of various flow paths and shapes

Fig. 9 B

Spiral flow path on the road

11 A heat storage device provided with the flow path

It is an object of the present invention to further adapt the capacity of the heat accumulators specified in the higher concepts to increase the load and no load power and to maintain the manufacturing cost more advantageously to the small and curved assembly space. The solution according to the invention is shown in the claims. It is corrugated or spiraled to pass through the accumulator core, and the wave and / or wavelength or coil shape may be irregular in the flow path and / or between the plurality of flow paths. The flow paths are in particular flat tubes, which may have internal inserts, for example. This is particularly advantageous when the flat tube consists of so-called plural cell tubes, for example as embedded in a condenser or evaporator. These tubes are easily bent into each shape without bending and folding, increasing the required turbulence of the thermoelectric wholesaler and the heat transfer area in the flat tubes.

The waveform of the flow path or the shape of the coil may be irregular. Where the fluctuations in the channel crest are severe, ie small, large or irregular in coil shape, the housing of the regenerator core and the entire regenerator is thus reduced or expanded. In this way, the heat accumulator is very advantageous to be applied to a highly curved assembly space without being a major manufacturing cost factor. For this reason, fabrication techniques for these corrugated or coiled flow paths exist in heat exchanger fabrication technology, and irregular wave height is only a matter of machine setting. Compared to the prior art with individual flat tubes, this has to be cut to different lengths and inserted into the tube base hole under complex conditions. All of this costs. The structure according to the invention requires only a small space called a collector and the flow path always enters the regenerator core and then comes out again. The space between the corrugations or coils of the flow path and the flow path is used as a space for filling the phase change material. As a result, the spatial relationship is changed to be a large space for the phase change material. This is furthermore the same as at least the large capacity regenerator of the regenerator, which is consistent with the optimum conditions. Exposing the space for the phase change material into a nearly complete corrugated steel sheet plays an important role for increasing the heat storage capacity. The liner also plays a negligible role for the stability of the heat accumulator.

The main advantage of the heat accumulator according to the invention is that the corrugated or helical flow path is relatively long and therefore bendable, while in the prior art it is better against temperature changes due to the tensile compressive load of the tube, which is fixed on the opposite side of the tube base. Tolerated. The load due to the metal coupling between the flow path and the heat accumulator core housing is generally smaller than in the prior art, so the risk of rupture is significantly reduced. Accordingly, the heat storage device according to the invention has more excellent durability and less detachment due to solder break. The main features and advantageous effects of the other cases are set forth in the specification of the following embodiments which are shown in the accompanying drawings. In these embodiments the invention is not limited in any case, as it is only useful as a aid to better understanding and design.

The latent heat accumulator 1 is mounted in the engine compartment of the vehicle. In this example, the engine coolant becomes a heat transfer medium and is circulated (not shown) by the coolant pump, and the potential heat accumulator 1 is connected to its mouth 2 outlet 3 opening therein. The heat insulating plate 4 may be highly vacuum insulated and may maintain this heat storage state under the same conditions for almost 50 hours or more for a phase change material that absorbs heat while being melted. When the engine is started, the coolant pump delivers cold coolant into the regenerator core 6 of the latent regenerator 1. At the same time, the coolant enters the regenerator together with the phase change material, which begins to crystallize and transfers its regenerator to the coolant. Rapidly heated coolant reduces fuel consumption by shortening the engine's start-up stage and can also be used for in-vehicle heating.

In the next stage of operation, the hot coolant dissipates its heat to the phase changer, which melts again and stores heat simultaneously. This conversion is repeated continuously so that the entire heat accumulator, in particular the flow path 5 and its joints, which here consist of a plurality of plain tube tubes 7, generates a large stress. However, since the flow path 5 is relatively long and easy to bend, and the corrugated steel sheet 8 is not so strong, most of the thermal expansion is corrected. Breakage of solder or weld joints is generally an exception.

The corrugated steel sheet 8 is disposed in the space 9, where the phase change material is considered. This space 9 is present between the waveform 10 of the flow path 5 and also the individual flow path 5. The corrugated steel sheet 8 arrangement is described in more detail below. The inlet (2) and outlet (3) also pass through each heat-absorbing tube located in the insulating plate (4) and remain static within the tube, where the hot coolant is less dense and stays on or inside the insulating plate. A cooling fluid layer is formed so as not to mix with the cooling water in the tube outside the heat insulating plate 4 having a high density. The tube end facing outward from the curved portion of the heat absorbing tube is a collecting space 12 inside which the tube ends of the four flow paths 5 join in the embodiment according to FIG. 1 and are connected there. . Before the tube ends join the collection space 12 they pass through the housing 11 of the heat accumulator core 6.

2 and 3 differ in that they differ in arrangement of the corrugated steel sheet 8 and the collection space 12. In addition, the heat accumulator of FIG. 2 is composed of an outer housing 14 of the heat accumulator 1 and a heat storage core 6 and a housing 11 containing a series of support elements 13 made of a non-heat conductive material. (14) is presented. The insulation space 4 is vacuum insulated and the supporting elements 13 keep the inner housing 11 and the outer housing 14 from contact with each other to maintain a high insulation efficiency. The thickness of the insulation plate 4 is only a few mm, thereby reducing the external dimension of the latent heat accumulator 1.

In FIG. 3, a long corrugated steel sheet 8 is used which surrounds the curved portion of the flow path 5 to minimize the number of components. On the other hand, in FIG. 2, it can be seen that the individual corrugated steel sheet 8 is disposed between the respective axes 10 of the flow path 5. In order to minimize the size of the heat accumulator 1, the collecting space 12 is only half shell type in FIG. The heat absorption type inlet 2 and the outlet 3 which are connected are not shown in this figure and the following figure.

4 and 6 show the formulation cross section of the heat accumulator 1 and FIG. 4 has an recessed recess 15 because the assembly space requires it. The flow path 5 shaft 10 is adapted to such an irregular shape and has a structure suitable for the recessed portion 15 therein. As a result, the irregularly-shaped shape of the heat accumulator 1 or the heat accumulator core 6 is relatively simple and can be sufficiently used as the flow path 5 and the phase change material space 9. An advantageous alternative is shown in FIG. 6 in which a collection space 12 is arranged in the heat accumulator core 6. On the other hand, the inner chamber of the heat accumulator core 6 which is covered by the corrugated steel sheet 8 in this manner is not very advantageous and can be used as the collecting space 12 while the insulating space 4 which is not shown here can be further reduced.

FIG. 5 is a principle diagram of the heat accumulator 1 in the direction of arrow A of FIG. 4. However, the collection space 12 is deployed to identify the plurality of chamber tubes 7 joining in the collection space 12. The plurality of chamber tubes 7 form a corrugated flow path 5, and a corrugated steel sheet 8 is interposed therebetween. FIG. 5 shows that the corrugated steel sheet 8 has a larger width than that of the plurality of chamber tubes 5. This causes the synchronization 16 of the corrugated steel sheet 8 to occur over the plurality of chamber tubes 7 or the flow passage 5, which further allows the phase change material space 9 to be formed between the corrugated steel sheets 5. 8) to be laid. The corrugated steel sheets 8 are fixed to the flow path 5, the outer steel sheet 8, and the inner housing 11 by soldering.

In the upper part of FIG. 5, the flow direction showing the heat absorbing portion and the cooling water coming out again from the inlet 2 through the outlet 3 is indicated.

7, 8 and 9 show a variety of possibilities for the shape of the heat accumulator 1 in a special manner and a structure suitable for each shape of the flow path 5 which is corrugated in this embodiment. FIG. 7 shows that the shaft 10 of the individual flow passage 5 has a completely different shaft height to fit the heat accumulator 1 with the recessed portion 15 and the convex portion 17. FIG. 9, which shows the cross-section B of FIG. 7, specifies that the shape is variable over three dimensions. Here, the plurality of chamber tubes 7 are built-in to form the flow path 5. The flow paths 5 are arranged in parallel with each other. Collecting space 12 is not shown in this figure.

The principle diagrams of FIGS. 10 and 11 show a heat accumulator 1 with a spiral flow path 5. The arrangement of the corrugated steel sheet 8 is suggested only in FIG. 10. They are not shown as they are between the coils 18 and between the outer coils 18 and the housing 11 as shown. The collection tube 12 is in the center of the regenerator 1 and the other collection space 12 is located around the regenerator core 6. At this time, the collection space 12 can be variably arranged at the same time. Accordingly, in another embodiment, not shown, the flow path 5 is formed spirally through the heat accumulator core 6, but has both collection spaces 12 around the heat accumulator core 6 (e.g., See FIG. 3 of DE 41 41 556).

In FIG. 11, the flow path 5 can respond to the conditions according to the shape of the various heat accumulator 1 by making h variable with respect to the height H of it. It is preferable that such flow path 5 also be a plurality of chamber tubes 7 in particular. Here, although the shape of the coil 18 between the flow paths 5 is different, in the flow path 5, the same, that is, the curved part is the same. Another embodiment, not shown, having a helical flow path 5, for example in accordance with FIG. 4, the coil 18 is configured such that the curved portions are formed differently so as to be suitable for the recessed part 15.

It is suitable as a car radiator that can be installed in small and complicated spaces while maintaining high power storage capacity while reducing manufacturing cost.

Claims (12)

The regenerators, in particular the latent regenerators, have at least the inlet and outlet of the heat transfer medium, which are fluidly coupled to the regenerator cores enclosed by the housing, in which flow paths (tubes) are arranged so that there is space between the flow paths and the phase change therein. Ash is contained and the flow path 5 is composed of approximately ellipse or flat tube so that it passes through the heat accumulator core 6 in a wave form and forms a space of the phase conversion material between the individual flow paths 5 and the individual flow paths 5. A heat accumulator, characterized in that at least generally cut into heat conducting elements (8), bonded to a toll (5) and to a metal, the corrugated thin strip has a width greater than the large diameter of the tubes constituting the flow path (5). Heat accumulators, in particular latent heat accumulators, have an insulator and at least an entry and exit space for the heat transfer medium, which are fluidly coupled to the heat accumulator core surrounded by the housing, in which flow paths (tubes) are arranged. The bar flow path (5) having a space therein and containing a phase change material therein is composed of ellipses or flat tubes spirally laid by the heat storage core (6), and the phase change material space (9) has individual flow paths ( 5) formed between the coils 18 of the individual flow paths 5, so that at least generally the thermally conductive element 8 is laid, which is joined to the metal by the flow paths 5, and the corrugated sheet strips are flow paths 5, respectively. Regenerator having a width larger than the large diameter of the tube forming a. The method of claim 1, An accumulator, characterized in that irregular wave heights and / or wavelengths are taken into account in the flow path (5) and / or between the plurality of flow paths (5) and / or between the plurality of flow paths (5). The method of claim 2, A regenerator characterized in that the shape of the coil (18) is irregular in the flow passage (5) and / or between the plurality of flow passages (5). According to the claim, The shaft (10) or the coil (18) extends in particular in the plane in the flow passage (5), wherein the plurality of flow passages (5) are in particular arranged approximately parallel to each other. The method according to any one of the preceding claims, The heat accumulator (1) is characterized in that it has a uniform appearance and the flow path (5) is suitable for this type. The method according to any one of claims 1 to 5, The heat accumulator 1 has a convex portion 17 or recess 15 or has a different shape than other uniform eg cylindrical or cuboid shapes and the flow path 5 (coil and / or shaft) has an angle of the heat accumulator 1. A heat accumulator, characterized in that it is adapted to the shape. According to the claim, The heat transfer element (8) located on the outside is characterized in that the heat accumulator core (6) is coupled to the housing (11) by metal. At least one of the preceding claims, The plate tube forming the flow path 5 is a plurality of chamber tubes (7). The method of claim 1, wherein The storage space 12 is characterized in that the heat storage is configured in a tubular shape. The method according to any one of claims 1 to 9, The storage space (12) is a heat storage, characterized in that configured in a substantially half-shell (shell) type. The method of claim 1, wherein The collection space (12) is characterized in that it is disposed in the heat insulator (4) or in the heat storage core (6).