JPH0631823U - Dehumidifier heat exchanger - Google Patents

Abstract

(57) [Summary] [Purpose] A heat exchanger for a dehumidifier that can reliably dehumidify even at a large flow rate without increasing the overall size and complexity of the configuration, and is also advantageous in maintenance. I will provide a. [Structure] In the dehumidifier heat exchanger, the evaporator 11,
12 is disposed in the dehumidifying cylinder 7, and the dehumidifying cylinder 7
A plurality of passage forming plates 13A and 13B extending alternately from the inner peripheral surface position toward the evaporators 11 and 12 are provided.
An air passage 23 meandering from the inlet of the dehumidifying cylinder 7 toward the outlet on the evaporators 11 and 12 is formed. The passage forming plate 13B on the most outlet side is formed so as to extend upward from the lower portion of the inner peripheral surface of the dehumidifying cylinder 7, and an opening 24 for passing water is formed at the lower end of the passage forming plate 13B.

Description

[Detailed description of the device]

[0001]

[Industrial applications]

 The present invention relates to a heat exchanger for a dehumidifier.

[0002]

[Prior art]

 In this type of dehumidifier heat exchanger, air passes through the evaporator in a meandering manner, whereby the air is cooled, moisture in the air is separated, and dehumidification is performed.

[0003]

[Problems to be solved by the device]

 However, in the conventional heat exchanger for dehumidifier, when the flow velocity of air becomes high, the separated water may be rolled up, and the water may be mixed into the dehumidified air again. Therefore, in the past, a large flow rate could not be obtained unless the heat exchanger was upsized.

Further, in some conventional heat exchangers, a filter is provided at the end of the meandering passage in order to ensure the water separation. However, this makes the structure complicated and heat exchange. The whole vessel will be enlarged.

Moreover, when the filter is provided, maintenance such as replacement and cleaning is required, and it is troublesome to handle. The object of the present invention is to provide a heat exchanger for a dehumidifier that can reliably dehumidify even at a large flow rate without increasing the overall size and complicating the configuration, and is also advantageous in maintenance. To do.

[0006]

[Means for Solving the Problems]

 Therefore, in the present invention, the evaporator is arranged in the dehumidifying cylinder, and a plurality of passage forming plates alternately extending from the inner peripheral surface position of the dehumidifying cylinder toward the evaporator are provided so that the upper part of the evaporator is dehumidified. In the heat exchanger for a dehumidifier in which an air flow path that meanders from the inlet to the outlet of the dehumidifier is formed, the passage forming plate on the most outlet side is formed so as to extend upward from the lower inner peripheral surface of the dehumidifying cylinder. The main point is that an opening for water passage is formed at the lower end of the.

[0007]

[Action]

 With the above configuration, the air passes through the evaporator formed in the dehumidifying cylinder and the passage formed by the plurality of passage forming plates alternately extending from the inner peripheral surface position of the dehumidifying cylinder toward the evaporator. That is, the air passes through the air passage that meanders from the inlet to the outlet of the dehumidifying cylinder to be cooled, and the moisture in the air is condensed. Then, the air is discharged from the gap on the uppermost side of the passage forming plate on the most outlet side, and the water is discharged from the opening on the lower side to separate them.

[0008]

【Example】

 An embodiment of the present invention will be described below with reference to the drawings. As shown in FIG. 1, the interior of the pressure-resistant container 1 is divided into three chambers 4, 5 and 6 by a disc-shaped partition plate 2 and an annular partition plate 3. A partition cylinder 7 as a dehumidifying cylinder is erected and supported between the partition plates 2 and 3, and the central chamber 5 is further partitioned by the partition cylinder 7 into a cooling chamber 5a and a precooling chamber 5b. The cooling chamber 5a communicates with the chamber 6. As shown in FIG. 2, the lowermost portion of the precooling chamber 5b is divided into a direction changing passage 5c by a pair of partition walls 8 and 9.

The inlets 8a and 9a are provided in the partition walls 8 and 9 on the partition plate 3 side, and the precooling chamber 5b communicates with the direction changing passage 5c through the inlets 8a and 9a. The suction pipe 10 is fixed to the lowermost part of the partition cylinder 7 on the partition plate 2 side so that the cooling chamber 5a communicates with the direction changing passage 5c via the suction pipe 10. The tip of the suction pipe 10 is formed to be inclined.

The refrigerating pipe 11 is disposed in the cooling chamber 5a so as to penetrate through the end wall 1a of the pressure resistant container 1. A large number of heat exchange fins 12 are supported side by side on the refrigeration pipe 11. The refrigerant is supplied into the freezing pipe 11, and the evaporator is composed of the freezing pipe 11 and the heat exchange fins 12.

The plurality of upper and lower passage forming plates 13 A and 13 B are inserted between the plurality of heat exchange fins 12 at a predetermined interval, and are joined and supported by the disengagement prevention bar 14. The upper passage forming plate 13A is inserted from the upper side, and the lower passage forming plate 13B is inserted from the lower side. The upper passage forming plates 13A and the lower passage forming plates 13B are alternately arranged to form the air passages 23.

As shown in FIG. 5, recesses 22 for pushing the fins 12 are formed in the passage forming plates 13A and 13B. The diameters of the passage forming plates 13A and 13B are slightly smaller than the inner diameter of the partition cylinder 7, and in this embodiment, a gap of 0.5 mm is formed between the passage forming plates 13A and 13B and the partition cylinder 7. . Further, an opening 24, which is an opening cut in a triangular shape, is provided below the lower passage forming plate 13B, and a passage 25 for water through which condensed water flows is formed.

Returning to FIG. 1, in the precooling chamber 5b, a plurality of heat transfer pipes 15 are erected and supported between the partition plates 2 and 3, and the chambers 4 and 6 are connected by the heat transfer pipe 15. . As shown in FIG. 7, arcuate passage forming plates 17, 18A, 18B are joined and supported by the heat transfer pipe 15. The heat transfer pipe 15 and the passage forming plates 17, 18A and 18B are joined by welding or expansion of the heat transfer pipe 15.

As shown in FIG. 2, both arc ends of the passage forming plate 17 are separated from the partition walls 8 and 9. As shown in FIG. 3, the passage forming plates 18A and 18B are symmetrically arranged in a separated state, and one arc end of the passage forming plates 18A and 18B is joined to the partition walls 8 and 9.

As shown in FIG. 1, an air inlet 19 and an air outlet 20 are provided at the uppermost portion of the pressure resistant container 1, and a drain outlet 21 is provided at the lowermost portion of the pressure resistant container 1. The drain discharge port 21 communicates with the chamber 6, and the air outlet 20 communicates with the chamber 4. The air inlet 19 communicates with the precooling chamber 5b, and the air inlet 19 and the air outlet 20 are adjacent to each other.

The hot and humid air enters the precooling chamber 5b through the air inlet 19 and meanders through the precooling chamber 5b as shown by the arrow in FIG. 7 by the direction changing action of the passage forming plates 17, 18A, 18B. The hot and humid air that has passed through the precooling chamber 5b enters the direction changing passage 5c through the inlets 8a and 9a, and heads for the suction pipe 10. That is, the air flow in the direction changing passage 5c flows in the opposite direction to the air flow in the precooling chamber 5b.

The high temperature moist air in the direction changing passage 5c enters the cooling chamber 5a via the suction pipe 10 and meanders by the direction changing action of the passage forming plates 13A and 13B as shown by the arrows in FIGS. While flowing between the heat exchange fins 12. That is, the airflow in the cooling chamber 5a flows in the same direction as the airflow in the precooling chamber 5b.

The air in the cooling chamber 5a is deprived of heat by the cooling action of the evaporator and becomes low in temperature. Water in the air is removed by this heat exchange action, and the air that has passed through the cooling chamber 5a becomes low-temperature dry air. The removed water collects at the bottom of the partition tube 7, passes through the passage 25 formed by the opening 24 of the lower passage forming plate 13B, and then from the opening 24 of the lower passage forming plate 13B at the end of the partition tube 7. It flows into the chamber 6. Then, it is discharged from the drain discharge port 21.

The low temperature dry air enters the heat transfer pipe 15 via the chamber 6 and heads for the chamber 4 side. Therefore, the high temperature moist air in the precooling chamber 5a is precooled by the low temperature dry air, and the precooled air enters the cooling chamber 5a via the direction changing passage 5c. The low temperature dry air exits the air outlet 20 after exiting the chamber 4.

That is, the inlet 19 of the precooling chamber 5b and the outlet of the heat transfer pipe 15 are arranged on one end side of the pressure vessel 1. The outlet side of the precooling chamber 5a and the inlets 8a and 9a of the direction changing passage 5c are arranged on the other end side of the pressure resistant container 1, and the outlet (the inlet 19) of the precooling chamber 5b is the inlet of the cooling chamber 5a ( It is connected to the suction pipe 10) by a direction changing passage 5c. The outlet of the cooling chamber 5a communicates with the inlet of the heat transfer pipe 15 through the chamber 6. With this configuration, the airflow in the precooling chamber 5b is countercurrent to the airflow in the heat transfer pipe 15.

The low-temperature dry air flow in the heat transfer pipe 15 is in the opposite direction (countercurrent) to the high-temperature moist air flow in the pre-cooling chamber 5b, and the temperature difference is larger than that in the case of flowing in the same direction. Can be taken. That is, the heat exchange rate in the counterflow is higher than that in the parallel flow, and the precooling degree of the high temperature moist air due to the counterflow is larger than that of the parallel flow. Therefore, the burden on the evaporator in the case of countercurrent precooling is smaller than that in the case of parallel flow precooling, and the temperature of the low-temperature dry air that has passed through the heat transfer pipe 15 rises, and the degree of drying further increases.

In this embodiment, the arrangement intervals of the passage forming plates 13A and 13B in the cooling chamber 5a can be changed. This means that the arrangement interval of the passage forming plates 13A and 13B affects the heat exchange rate in the cooling chamber 5a. This is because they are considering doing. When the interval between the passage forming plates 13A and 13B is narrowed, the flow velocity of air in the cooling chamber 5a is increased, and the heat exchange rate is increased. That is, the temperature of the low temperature dry air is reduced by narrowing the arrangement interval of the passage forming plates 13A and 13B. Therefore, even if the air flow rate is increased, if it is desired to make the degree of drying of the low temperature dry air the same, the arrangement interval of the passage forming plates 13A and 13B may be narrowed, and this modification is possible in this embodiment.

The water separated from the hot and humid air in the precooling chamber 5b accumulates in the direction changing passage 5c, and the water level in the direction changing passage 5c rises. Due to this rise in water level, the cross-sectional area of passage in the direction changing passage 5c decreases, and the air flow velocity increases. The water in the direction changing passage 5c is sucked up from the suction pipe 10 into the cooling chamber 5a by the increase in the air flow velocity. The water sucked up to the cooling chamber 5a is discharged to the chamber 6 and the drain outlet 21 side along the inner bottom surface of the partition cylinder 7.

Although the tip of the suction pipe 10 is inclined, the degree of this inclination affects the quality of drain discharge. That is, if the inclination angle θ is too small, the siphoning frequency decreases and the siphoning water becomes large water droplets and enters the cooling chamber 5a. When the water droplets that have entered the cooling chamber 5a are scattered, the scattered water travels along the airflow and enters the heat transfer pipe 15, resulting in uneven drying. On the other hand, if the degree of inclination is too large, the amount of drain accumulated in the direction changing passage 5c increases, and rust is likely to occur.

As described above, in the dehumidifier heat exchanger of this embodiment, the air passage 23 and the moisture passage 25 are separated by the lower passage forming plate 13B arranged at the end of the partition cylinder 7. The water separated from the cooling chamber 5a is prevented from scattering. Therefore, even if the flow velocity of the air increases, moisture is not mixed in the air sent to the heat transfer pipe 15, and a predetermined dew point can be realized. Further, since the water passage 25 is formed by cutting out the triangular opening 24 at the lower portion of the lower passage forming plate 13B, the air and condensed water can be separated at low cost.

The present invention is not limited to the configuration of the above embodiment, and for example, a special pipe having a high heat exchange rate may be used as the heat transfer pipe 15. Further, it is also possible to embody it by arbitrarily changing it within a range not departing from the gist of the present invention, such as providing a filter at the inlet of the heat transfer pipe 15.

[0027]

[Effect of device]

 According to the present invention, the condensed water and the air are separated from each other by the passage forming plate, so that the water is not scattered and does not flow into the heat transfer pipe. Therefore, there is an effect that the dew point is not affected by moisture and the flow rate can be increased to 1.5 times that of the conventional case. Furthermore, since an opening is formed in one passage forming plate, the upper portion of the passage forming plate serves as an air outflow passage, and the opening serves as a moisture passage, it is possible to inexpensively separate air and moisture.

[Brief description of drawings]

FIG. 1 is a longitudinal sectional view showing an embodiment embodying the present invention.

FIG. 2 is a sectional view taken along the line AA of FIG.

FIG. 3 is a sectional view taken along line BB of FIG.

4 is a cross-sectional view taken along the line CC of FIG.

5 is a cross-sectional view taken along the line DD of FIG.

6 is a cross-sectional view taken along the line EE of FIG.

FIG. 7 is a perspective view showing a passage forming plate in the precooling chamber.

FIG. 8 is a perspective view showing a passage forming plate in the cooling chamber.

[Explanation of symbols]

Reference numeral 7 ... Partitioning cylinder that is a dehumidifying cylinder, 11 ... Refrigerating pipe that constitutes the evaporator, 12 ... Heat exchange fin that constitutes the evaporator, 13
A, 13B ... Passage forming plate, 23 ... Air flow path, 24 ... Opening part which is an opening.

Claims (1)

[Scope of utility model registration request] 1. An evaporator is provided in the dehumidifying cylinder, and a plurality of passage forming plates extending alternately from the inner peripheral surface of the dehumidifying cylinder toward the evaporator are provided so that the evaporator has a dehumidifying cylinder. In the heat exchanger for a dehumidifier in which an air flow path meandering from the inlet to the outlet is formed, the passage forming plate on the most outlet side is formed so as to extend upward from the lower inner peripheral surface of the dehumidifying cylinder, and the passage forming plate A heat exchanger for a dehumidifier, characterized in that an opening for passing water is formed at the lower end.