JPH0366594B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to improvements in heat exchange devices used in rotary air conditioning ventilation fans and the like.

Conventional Structure and Problems There are two types of conventional total heat exchange systems: a heat storage rotation type that utilizes heat and moisture stored in a rotor, and a static transmission type that performs total heat exchange through a partition plate. The heat storage rotary type has a small heat storage capacity of the rotor, so it is usually about 15
A rotational speed of the rotor on the order of revolutions per minute is required. Therefore, sliding noise is likely to occur due to rotation. Furthermore, there is a drawback that the effective amount of moisture adsorption to the element is reduced due to the effects of sensible heat storage in the rotor and heat of adsorption and desorption of moisture.

On the other hand, in the static permeation type, sensible heat exchange and latent heat exchange are performed only by the heat conduction mechanism in the partition plate and the moisture permeation phenomenon, so the total heat exchange efficiency is generally low. Furthermore, both of the above types of total heat exchangers can perform only a single function of total heat exchange.

Purpose of the Invention: It is more efficient than conventional heat exchangers, has multiple functions such as being able to be used as a sensible heat exchanger, and requires less rotation than conventional heat storage rotary types.
The present invention provides a heat storage/transmission rotary heat exchanger having a feature of low sliding noise.

Structure of the Invention A cylindrical rotor in which a plurality of layers of moisture-impermeable, hygroscopic partition walls are stacked circumferentially at intervals, and a primary airflow and a secondary airflow are formed to pass alternately between these layers. By rotating this element, a total heat exchange method is adopted in which the primary airflow and secondary airflow are periodically exchanged and passed through each layer between the partition walls. The heat generated on the surface of the element due to adsorption and desorption of heat and moisture is not transferred to the other side only by the rotation of the rotor, but a certain amount of the heat can be transferred to the other side by heat conduction in the partition wall. Therefore, compared to conventional rotary total heat exchange equipment, the rotation speed can be lowered and sliding noise can be reduced. Furthermore, since the effective amount of moisture adsorbed to the element increases, the heat exchange efficiency increases. Furthermore, in this configuration, compared to the conventional static permeation type total heat exchange method, a heat storage and moisture storage mechanism is added to the heat exchange mechanism, so efficiency can be further increased by selecting the rotation period of the rotor.

In addition to these features, the new system can function as a sensible heat exchanger by stopping the rotation of the rotor. This means that a new function is added compared to the conventional total heat exchange method.

DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments of the present invention will be described based on the drawings. FIG. 1 shows a partial schematic appearance of a cylindrical rotor according to an embodiment for realizing the heat exchange method of the present invention,
FIG. 3 is a diagram showing related gas inflow and outflow paths. In the figure, reference numeral 1 indicates a cylindrical rotor, and reference numeral 2 indicates an inner cylindrical portion of the rotor, which is provided with an air flow passage switching section as will be explained later.
3 is a separator that separates both air flows. In the case of the rotor 1 having this structure, airflow entering the rotor 1 from one side of the separator 3 exits the rotor 1 from the same side of the separator 3.

As shown in FIG. 2, this rotor 1 includes a first element 4 having a passage passing through in the axial direction of the cylinder;
A second element 5 having a passage communicating between two openings of the inner cylindrical part through which airflow enters and exits in a radial direction perpendicular to this is laminated on each other in the circumferential direction via a partition wall 6. ing.

FIG. 3 shows an example of elements constituting such a rotor 1, in which a pair of basic elements 7 and 8 are stacked alternately to constitute the rotor 1. In this case, colloidal silica is applied as a moisture absorbent to the surface of the vinyl chloride plate on which the basic elements 7 and 8 are molded, and is dried and adhered thereto. The airflow passage in this basic element 7 passes through the cylinder axis direction, and the basic element 8
The passage inside the tube enters from one of the inlets on the inner cylinder side and exits from the other outlet on the inner cylinder side.

FIG. 4 shows another embodiment of the basic elements constituting the rotor 1. In FIG. In this case, the partition wall 6 of the basic element 9
Although the spacing between them varies in the radial direction, the passage spacing of the basic element 10 is constant, so that the resistance of the passages in the basic element 10 is characteristically smaller than in the case of the basic element 8.

FIG. 5 is a schematic cross-sectional view of the heat exchanger of this embodiment when such a cylindrical rotor 1 is used, and schematically shows the flow of air within the heat exchanger.

In the figure, numerals 11 and 12 are separators that separate the paths of both air flows entering the rotor 1. This uses a single partition plate 15 whose both ends are twisted by 180 degrees around the central portion of the partition plate 15, but other configurations may be used. 13,
Reference numeral 14 denotes an air flow passage switching section provided at the entrance and exit of the inner cylinder side air flow passage, which basically has a structure as shown in FIG. 6 and corresponds to the area between x ₁ and x ₂ of the air flow passage. In the figure, the partition plate 15 that separates the air flow paths between x ₁ and x ₂ is rotated by 180 degrees, so that the air flow paths on both sides of the partition plate 15 switch places at this portion. In this structure, the only parts that rotate around the cylinder axis during heat exchange are the rotor 1 and the partition part 16 that is integrated with the rotor 1, and the separators 11 and 12 and the airflow passage switching part 1
3 and 14 are fixed and do not move.

The heat exchange between the two air streams is not only performed through the partition wall 6 between the first element 4 and the second element 5 in FIG. 2, but also due to the rotation of the rotor 1, for example, As shown in the figure, on the upper surface of the rotor 1, airflow B flows through the first element 4 and airflow A flows through the second element 5, but on the lower surface, airflow A flows through the first element 4, and airflow A flows through the first element 4. The second element 5 has airflow B, and by repeatedly exchanging each other, the sensible heat and moisture stored in the element transfer to the other airflow, thereby performing total heat exchange. .

Compared to conventional heat storage rotary total heat exchangers, the advantage of this method is that it does not rely solely on the rotation of the rotor to absorb the heat of adsorption and desorption that occurs when moisture is adsorbed and desorbed into the element, or the sensible heat in the high-temperature air flow. Since most of the water can be transferred through the partition wall 6 between the first element 4 and the second element 5, the effective amount of moisture adsorbed by the element can be increased and efficiency can be increased. Furthermore, the heat storage capacity of the element does not reach saturation even when the rotor 1 is stationary due to sensible heat transfer through the partition wall 6, so the rotational speed of the rotor can be lowered compared to the conventional rotary type. The optimal rotation speed for conventional heat storage rotary systems is around 15 revolutions per minute, but experimental results show that the optimal rotation speed for the new system is around 1 revolution per minute. This is the reason why the new system produces less sliding noise due to rotation than the conventional rotary type. Furthermore, this method can obtain data with higher efficiency than the conventional static transmission method. This is thought to be because the sensible heat exchange mechanism in the stationary transmission type is conduction only, but in the new type it relies on both conduction and heat storage mechanisms.

FIG. 7 is a diagram showing a schematic appearance of a cylindrical rotor according to another embodiment for realizing the heat exchange method of the present invention and related gas inflow and outflow paths. In this embodiment, as shown in FIG. 8, the rotor 17 includes a first element 18 having an opening 23 on one end side 23 in the cylinder axis direction and an opening 24 on the inner cylinder side near the other end; a second element 19 having an opening 26 at the other end 25 in the cylinder axis direction and at the inner cylinder side opposite thereto;
are stacked on each other in the circumferential direction with partition walls 20 in between. Figure 9 shows the rotor 17 in this case.
This is an example of the elements constituting the basic element 2.
The rotor 17 is constructed by stacking pairs of rotors 1 and 22 alternately. The basic elements 21 and 22 in this case are molded vinyl chloride plates with Al ₂ O ₃ as a moisture absorbent on the surface.
It was dried after being applied. In a rotor in which such basic elements 21 and 22 are laminated, the direction of the airflow inside is changed by 90 degrees.
Both passages have the same passage resistance. Since the wind pressure between both air flow passages becomes equal, the heat exchange rate due to heat transfer is improved.

FIG. 10 is a schematic cross-sectional view of a heat exchanger using the rotor 17 of this example, which schematically shows the flow of air within the heat exchanger. Even in a case like this example, the heat exchange mechanism is the same as the heat exchange mechanism in the case of the airflow passage of the rotor 1.

Figure 11 shows the heat exchanger shown in Figure 5 used at 35℃ and 60℃.
%, 25°C, 50% air flow rate of 2 m ³ /min, heat exchange efficiency between both air flows was obtained by changing the rotational speed of the rotor. In the figure, A is the total heat exchange efficiency, B is the sensible heat exchange efficiency, and C is the latent heat exchange efficiency. As can be seen from this data, in this system, when the rotation is stopped, it functions as a sensible heat exchanger, and as the rotation speed increases, the humidity exchange efficiency tends to decrease. This indicates that this heat exchange system has the potential to support more sophisticated air conditioning by changing the rotation speed. For comparison, FIG. 12 shows similar experimental data in the case of a conventional heat storage rotary type, and the elements have a structure in which corrugated kraft paper is spread in the shape of a rotor. In this case, as shown in the data, even if the rotor speed changes, the ratio of sensible heat exchange efficiency and latent heat exchange efficiency to the total heat exchange efficiency does not change as much as in the heat storage transmission method. .

Effects of the Invention As described above, in the heat exchange device of the present invention, the total heat exchange efficiency can be increased compared to the conventional method. Further, by stopping the rotation of the rotor, the total heat exchanger can be used as a sensible heat exchanger. Furthermore, the ratio between sensible heat exchange efficiency and latent heat exchange efficiency can be changed by controlling the rotation speed. These features make an air conditioner using the heat exchange device of the present invention more suitable for energy saving. Further, since the present invention has a hollow portion, a heat exchange airflow can flow between the end face of the cylinder and the hollow portion without using the outer periphery, and the installation area may be small. In addition, since the effective area for heat exchange is small in the central part of the cylinder, even if this part is removed, the heat exchange function will not be impaired compared to a cylinder having the same external shape.

[Brief explanation of drawings]

FIG. 1 is a partial schematic explanatory diagram of a cylindrical rotor according to an embodiment for realizing the heat exchange device of the present invention, FIG. 2 is a partial detailed diagram of FIG. 1, and FIG. 3 is a configuration of the rotor. 4 is a perspective view of another embodiment of the basic element, FIG. 5 is a schematic cross-sectional view of a heat exchange device according to an embodiment of the present invention, and FIG. 6 is an air flow passage exchange section. , FIG. 7 is a partial schematic illustration of a cylindrical rotor according to another embodiment of the present invention, FIG. 8 is a partial detailed view of the rotor of FIG. 7, and FIG. 9 is a configuration of the rotor. FIG. 10 is a schematic cross-sectional view of a heat exchange device according to a different embodiment of the present invention; FIG. 11 is a diagram showing the heat exchange efficiency between both air streams using the heat exchange device of FIG. 5; FIG. 12 is a diagram showing the heat exchange efficiency of the conventional heat storage rotary type for comparison with the data shown in FIG. DESCRIPTION OF SYMBOLS 1... Rotor, 2... Inner cylindrical part, 3... Separator, 4, 5... Element, 6... Partition wall, 7
~10... Basic element, 11, 12... Separator, 13, 14... Air flow passage switching section.

Claims (1)

[Claims] 1. A hollow cylinder is formed by alternately stacking first and second elements having heat storage and moisture storage properties, and the partition wall existing between the first and second elements is non-permeable. at least a portion of the material constituting the element is hygroscopic, one of the elements is a primary air flow path, the other element is a secondary air flow path, and at least one end of the hollow part of the cylindrical heat exchanger An airflow passage switching section is provided in the cylindrical heat exchanger, and the sensible heat exchange function is performed when the cylindrical heat exchanger is in a stationary state, and the primary airflow passage and the secondary airflow passage are periodically exchanged by rotating the cylindrical heat exchanger. A heat exchanger characterized by obtaining a total heat exchange function. 2 The first element has an airflow passage hole in the cylindrical axial direction, and the second element has a plurality of openings with respect to the hollow part, and the airflow passes from one opening to the other opening. A heat exchange device according to claim 1, which enables the heat exchange device according to claim 1. 3 The first element communicates from one end of the cylindrical heat exchanger to the hollow part via an axial passage, and the second element communicates from the other end of the cylindrical heat exchanger to the hollow part via an axial passage. 2. The heat exchange device according to claim 1, further comprising a passage leading to the heat exchanger. 4. The heat exchange device according to claim 2 or 3, wherein a separator is interposed in the diametrical direction of the cylindrical heat exchanger to divide the cylindrical heat exchanger and the hollow portion into two. 5. The heat exchange device according to claim 1, wherein the air flow passage switching section has a shape in which the center line of a stretchable flat plate is aligned with the axis of the cylindrical heat exchanger, and both ends are twisted by 180 degrees.