JP2006003001A - Air temperature adjusting machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To sufficiently reduce uneven distribution of a flow rate of the air flow passing through heat exchangers and to properly uniformize the same. <P>SOLUTION: A bathroom heater 1 comprises the heat exchangers 7, 9 mounted on positions to allow the air flow flowing from an air suction port 11 to an air blow-off port 15 to cross them. The heat exchangers 7, 9 are respectively provided with a plurality of fins 91a, 91b, 92 arranged in parallel with each other at intervals, and heating medium tubes 97 penetrating through the fins approximately in the orthogonal direction at several parts of each fin. Each of the fins 91a, 91b, 92 is provided with a plurality of cut/raised pieces 94 extended in the direction crossing the air flow, and the draft resistance by the cut/raised pieces determined by the combination of the total length of the cut/raised pieces of the fin per a unit area and a rising height of the cut/raised piece is divided into three or more stages in the entire heat exchanger with the relationship that the farther a distance from a draft fan is, the lower the draft resistance is. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an air temperature adjuster including a heat exchanger. Specifically, the present invention relates to an air temperature adjuster that improves heat exchange performance by suppressing the occurrence of bias in the flow velocity distribution of the airflow that passes through the heat exchanger.

An air temperature regulator equipped with a heat exchanger includes a housing having an air inlet and an air outlet, a blower fan accommodated in the housing, and air flowing from the air inlet to the air outlet through the air blower fan. It is equipped with a heat exchanger that is arranged at a position where the flow crosses. The heat exchanger includes a plurality of fins arranged in parallel at intervals, and a heat medium pipe penetrating each fin in a substantially right angle direction at a plurality of positions of the fins.
The air temperature adjuster operates the blower fan in a state where the heat medium is flowing through the heat medium pipe, and allows the air flow to pass between the fins. For example, when the blower fan is operated in a state where warm water is flowing through the heat medium pipe, the heated air is blown out from the outlet through heat exchange with the fin heated by the warm water. Or if a ventilation fan is drive | operated in the state in which cold water is flowing, the air cooled by exchanging heat with the fin cooled with cold water will blow off from a blower outlet.
In order to improve the heat exchange efficiency between the fin and air, a technique of cutting and raising the fin to form a piece is known. A plurality of cut and raised pieces are formed on each fin, and each cut and raised piece is formed to extend in a direction crossing the air flow.

  The density and height of the cut and raised pieces greatly affect the ventilation resistance and heat exchange efficiency of the heat exchanger. The cut and raised piece extends in a direction crossing the air flow. Therefore, for each unit area of the fin, the lengths of the cut and raised pieces extending in the direction crossing the air flow can be summed up. If the overall length of the cut and raised pieces per unit area of the fin is long, the heat exchange efficiency is improved, but the ventilation resistance is increased. If the overall length of the cut and raised piece per unit area of the fin is short, the heat exchange efficiency is lowered but the ventilation resistance is reduced. If the standing height of the cut and raised piece is high, the heat exchange efficiency is improved, but the ventilation resistance is increased. If the standing height of the cut and raised piece is low, the heat exchange efficiency is lowered, but the ventilation resistance is reduced. The ventilation resistance and heat exchange efficiency by the cut and raised pieces are determined by a combination of the total length of the cut and raised pieces per unit area of the fin and the standing height of the cut and raised pieces.

In order to improve the heat exchange performance of the heat exchanger, it is preferable to make the flow velocity distribution of the air flow passing through the heat exchanger uniform. If the flow rate is low in a part, heat exchange becomes inactive in that part, and the heat exchange performance of the entire heat exchanger decreases.
Japanese Patent Application Laid-Open No. H10-228688 discloses a technique for making the flow velocity distribution of the air flow passing through the heat exchanger uniform. Patent Document 1 describes a technique for preventing water droplets generated by heat exchange from being cut up and staying between pieces and increasing the airflow resistance due to the water droplets. This document discloses a technique for dividing the combination of the total length of the cut and raised pieces formed per unit area of the fin and the raised height of the cut and raised pieces into two stages at the upper and lower stages of the fins. . Specifically, in the upper stage of the fin, the raised height of the cut piece is increased. At the lower stage of the fin, the raised height of the cut piece is lowered. Regarding the total length of the cut and raised pieces formed per unit area of the fin, there are described an example in which the upper and lower tiers are kept the same, and an example in which the total length in the lower tier is shorter than the total length in the upper tier. ing.
In the technique of Patent Literature 1, water drops are easily dropped by lowering the standing height of the cut and raised pieces at the lower stage of the heat exchanger. According to this technology, it is possible to prevent water droplets from adhering to the fins at the lower stage of the heat exchanger, and to suppress increase in ventilation resistance at the lower stage of the heat exchanger due to the adhering water drops, and the air flow passing through the heat exchanger The flow velocity distribution can be made uniform.
JP-A-9-105594

  In order to improve the heat exchange performance of the heat exchanger, it is preferable that the flow velocity distribution of the air flow passing through the heat exchanger is as uniform as possible. In the technique described in Patent Document 1, the combination of the total length of the cut and raised pieces per unit area of the fin and the raised height of the cut and raised pieces is divided into two stages, thereby providing a flow velocity distribution of the air flow. We are trying to make it uniform.

If the wind pressure distribution applied to the heat exchanger is uniform, the combination of the total length of the cut and raised pieces per unit area of the fin and the raised height of the cut and raised pieces is divided into two stages to adhere to the fins. It is possible to compensate for the deviation of the flow velocity distribution of the air flow passing through the heat exchanger due to water droplets, and to make the flow velocity distribution uniform to a considerable extent.
However, the flow velocity distribution of the air flow obtained by the blower fan provided in the air temperature adjuster is not uniform within the housing and often varies depending on the location. The wind pressure applied to the heat exchanger is unevenly distributed.
If the wind pressure applied to the heat exchanger is unevenly distributed, the combination of the total length of the cut and raised pieces per unit area of the fin and the raised height of the cut and raised pieces can be divided into two stages. Unevenness of the flow velocity distribution of the air flow passing through the exchanger cannot be compensated, and the degree of uniformity is low.
In particular, recent air temperature regulators have been downsized and housed a blower fan and a heat exchanger in a narrow space, so the wind pressure distribution applied to the heat exchanger often varies greatly depending on the location of the heat exchanger, Even if the combination of the total length of the cut and raised pieces per unit area of the fin and the raised height of the cut and raised pieces is divided into two stages, it cannot compensate for the uneven flow velocity distribution of the air flow passing through the heat exchanger. The degree of uniformity is low.
In the present invention, there is provided a technique that sufficiently suppresses the deviation of the flow velocity distribution of the air flow passing through the heat exchanger and makes it uniform uniformly.

(Means for solving the problem)
An air temperature regulator embodied by the present invention includes a housing having an air inlet and an air outlet, a blower fan accommodated in the housing, and air flowing from the air inlet to the air outlet through the air blower fan. It is equipped with a heat exchanger that is arranged at a position where the flow crosses. The heat exchanger includes a plurality of fins arranged in parallel at intervals, and a heat medium pipe penetrating each fin in a substantially right angle direction at a plurality of positions of the fins.
Each fin is formed with a plurality of cut and raised pieces extending in the direction crossing the air flow, determined by the combination of the total length of the cut and raised pieces per unit area of the fin and the raised height of the cut and raised pieces The ventilation resistance due to the cut and raised pieces is lower as it is farther from the blower fan, and is divided into three or more stages in the entire heat exchanger.
If the cut and raised pieces are not formed within the unit area of the fin, the total length of the cut and raised pieces is zero. When the ventilation resistance by the cut and raised pieces is divided into three or more stages, the one division may be a stage that “the cut and raised pieces are not formed”. If the combination of the total length of the cut and raised pieces per unit area of the fin and the standing height of the cut and raised pieces is divided into three or more stages, the total length is constant and the standing height is three or more stages. The standing height may be constant and the total length may be divided into three or more stages, or the total length and the standing height may be divided into two stages. It may be divided into three or more stages by combining them. The unit area is obtained by dividing the longitudinal direction of the fin into a size that is at least the longest cut and does not divide the piece, and a range smaller than that should not be the unit area.

(The action and effect)
In the heat exchanger provided in the air temperature controller, the ventilation resistance by the cut and raised pieces is divided into three or more stages according to the combination of the total length of the cut and raised pieces and the standing height of the cut and raised pieces.
The flow velocity of the air flow that passes through the heat exchanger depends on the ventilation resistance of the air flow path from the intake port through the heat exchanger to the outlet, and is slow in the air flow path with high ventilation resistance and low in ventilation resistance. Fast in the air flow path. It is not easy to check the airflow resistance of the air flow path from the air intake port through the heat exchanger to the air outlet, and the airflow resistance due to the cut piece is adjusted stepwise to pass through the heat exchanger from the air intake port. Thus, it is difficult to equalize the ventilation resistance of the air flow path leading to the outlet.
The present inventor has found that the airflow resistance of the air flow path from the intake port through the heat exchanger to the blowout port is basically determined by the distance from the blower fan to the heat exchanger. In other words, the resistance to airflow from the air inlet to the outlet of the airflow passing through the heat exchanger at a position far from the blower fan is high, and the airflow passing through the heat exchanger at a position near the distance from the blower fan is high. It was found that the draft resistance from the inlet to the outlet was low.
In the present invention, the entire heat exchanger is divided into three or more regions in accordance with the distance from the blower fan. A combination of the total length of the cut and raised pieces and the standing height of the cut and raised pieces is adopted. A combination of the total length of the cut and raised pieces and the standing height of the cut and raised pieces is adopted so that the ventilation resistance by the cut and raised pieces is reduced in a region far from the blower fan.
According to the above, regardless of the location in the heat exchanger, the flow resistance of the air flow passing through the heat exchanger is made uniform by equalizing the airflow resistance of the air flow path from the inlet port through the heat exchanger to the outlet port. Distribution is made uniform. It is possible to actively exchange heat using the entire heat exchanger. The air temperature adjuster of the present invention has high heat exchange efficiency and high air temperature adjustment capability.

(Preferred means for solving the problem)
The heat exchanger may be divided into a plurality of plane portions so as to form a part of a polygon surrounding the blower fan when observed from the axial direction of the blower fan having a substantially cylindrical outer shape. .
In this case, the ventilation resistance determined by the combination of the total length of the cut and raised pieces per unit area of the fin and the raised height of the cut and raised pieces is so low that the ventilation resistance is closer to the vertex of the polygon. The entire vessel is preferably divided into three or more stages.

(The action and effect)
In order to make the air temperature controller compact, the heat exchanger is often divided into a plurality of flat portions and arranged so as to constitute a part of a polygon surrounding a blower fan having a substantially cylindrical outer shape. . In this case, the apex (the apex here includes the part that forms the apex if there is an adjacent plane, that is, the part that is terminated because there is no adjacent plane) is far from the blower fan. Become.
If the combination of the total length of the cut-and-raised piece and the standing height is divided into three or more stages, the ventilation resistance of the cut-and-raised piece is lower as it gets closer to the apex. Thus, the ventilation resistance of the air flow path from the intake port through the heat exchanger to the blowout port is made uniform, and the flow velocity distribution of the air flow passing through the heat exchanger is made uniform. It is possible to actively exchange heat using the entire heat exchanger. The air temperature adjuster of the present invention has high heat exchange efficiency.

The best mode for carrying out the invention is listed below.
(Mode 1) The air temperature adjuster is a ceiling-embedded heater.
(Mode 2) The air temperature adjuster is a wall-mounted heater.
(Mode 3) Hot water circulates through the heat medium pipe of the heat exchanger.
(Mode 4) The heat medium pipe of the heat exchanger is connected to a water heater.
(Embodiment 5) The fins of the heat exchanger have notches for blocking heat transfer from the upper heat medium tube to the fins and heat transferred from the lower heat medium tube to the fins from each other. Is provided.
(Embodiment 6) The rising height of each cut and raised piece formed on the fin is constant, and the ventilation resistance due to the cut and raised piece is only due to the difference in the total length of the cut and raised piece per unit area of the fin. The entire heat exchanger is divided into three or more stages.

(First Embodiment) A first embodiment of an air temperature regulator embodying the present invention will be described with reference to the drawings.
FIG. 1 is an external view of a ceiling heating type bathroom heating device 1. The bathroom heating apparatus 1 is an example of an air temperature regulator that heats a bathroom by blowing hot air. An air inlet 11 and an air outlet 15 are formed on the lower surface of the housing 3 of the bathroom heating device 1.

A II-II cross-sectional view of the bathroom heating device 1 of FIG. 1 is shown in FIG. FIG. 2 mainly shows components related to the present invention, and components included in a normal ceiling-embedded bathroom heating device are omitted as appropriate.
The bathroom heating device 1 includes a heat exchanger 7, a heat exchanger 9, and a sirocco fan 17 inside the partition plate 5 of the housing 3. The air inlet 11 and the air outlet 15 formed on the lower surface of the housing 3 are partitioned by a partition plate 13.
The heat exchanger 7 and the heat exchanger 9 constitute a part of a polygon surrounding the sirocco fan 17 when observed from the axial direction of the substantially cylindrical sirocco fan 17. The heat exchanger is divided into a plurality of flat portions 7 and 9 and is bent at a bent portion 8 to form a substantially V shape. The heat exchanger 7 is disposed to be inclined above the heat exchanger 9, and the upper short side is in contact with the partition plate 5. The heat exchanger 9 is horizontally disposed above the air suction port 11 and faces the air suction port 11. The sirocco fan 17 has a substantially cylindrical outer shape, is disposed at a position on the side of the heat exchanger 7 and above the heat exchanger 9, and blows an air flow to the air outlet 15. The air sucked from the air inlet 11 by the sirocco fan 17 passes through the heat exchanger 7 or the heat exchanger 9 and is heat-exchanged and heated, and then blown out from the air outlet 15 by the sirocco fan 17. .

The heat exchangers 7 and 9 will be described in detail with reference to FIG. FIG. 3 shows the heat exchanger 9. Since the basic configuration of the heat exchangers 7 and 9 is the same, the description of the heat exchanger 7 is omitted in the description of the heat exchanger 9.
As shown in FIG. 3 (1), the heat exchanger 9 includes mounting plates 91 a and 91 b and a plurality of inner fins 92. The attachment plates 91a and 91b are formed of an iron plate, a stainless steel plate, an aluminum plate, or the like. A flange protruding outward is provided at the upper end of the long side and the lower end of the long side of the mounting plates 91a, 91b, and the strength of the outer side of the heat exchanger 9 is improved. The inner fin 92 is formed of an aluminum plate. The inner fins 92 are not provided with flanges, and are arranged in parallel at intervals extending in parallel with the ventilation direction.
The mounting plates 91a and 91b and the inner fins 92 are provided with a plurality of through holes 93 at predetermined intervals. A heat medium pipe 97 is inserted and fixed in these through holes 93 (only a part of the heat medium pipe 97 is shown in FIG. 3A). A heat medium for heat exchange circulates in the heat medium pipe 97. In the present embodiment, one heat medium tube 97 is used, and the heat medium tube 97 is arranged in parallel by being bent in a U shape in the vicinity of the outside of the mounting plates 91a and 91b. In this embodiment, the heat medium pipe 97 passes through a series of through holes 93 provided on the lower side of the mounting plate and fins from the right to the left, and continues through the left end through hole 93 and then continues to the mounting plate. Or through a series of through-holes 93 provided on the upper side of the fin from left to right. The heat medium flows from right to left in the heat medium pipe 97 that passes through the through holes 93 on the lower side of the mounting plate and fins, and then passes through the group of through holes 93 on the upper side of the mounting plate and fins. It moves to 97, and this time flows from left to right. A water heater (not shown) is connected downstream of the heat medium pipe 97 passing through the upper right through hole 93. Hot water heated to a temperature at which heat exchange can be performed again by the water heater is returned to the heat medium pipe 97 and circulated.

As shown in FIG. 3B, a plurality of cut and raised pieces 94 are formed on the surface of the inner fin 92 in order to improve the heat exchange performance of the heat exchanger 9. The cut and raised sides 94 are formed as a set of a predetermined number for each section sandwiched between adjacent through holes 93. As shown in the enlarged perspective view of FIG. 4A, the cut-and-raised piece 94 is formed so as to protrude to one side from a cut hole 96 formed in the fin surface. The standing height of each raised and raised piece 94 is constant. Each cut and raised piece 94 extends long in a direction crossing the air flow.
The lower cut and raised piece on the long side of the cut and raised piece 94 is substantially orthogonal to the ventilation direction (the short side direction of the fin) indicated by the arrow p. As shown in the sectional view of FIG. 4 (2), the cut and raised piece 94 has an upper cut and raised piece 94a and a lower cut and raised piece 94b in the projecting portion that are open and penetrated. Cross both sides of the piece 94.

As shown in FIG. 2, in the heat exchanger 7 and the heat exchanger 9 of the bathroom heater 1, the number of cut and raised pieces 94 formed in a section sandwiched between adjacent through holes 93 is one. It is not like. Specifically, (1) A1 portion of the heat exchanger 7, A2 portion of the heat exchanger 7, and A3 portion of the heat exchanger 9 are not formed with the cut and raised pieces 94. (2) Heat exchange Two cut-and-raised pieces 94 are formed as a set in the B portion of the vessel 7, and (3) five cut-and-raised pieces 94 are formed as a set in the C portion of the heat exchanger 9. That is, the number of cut and raised pieces 94 is divided into three stages (1) to (3).
In the present embodiment, the total length of the cut and raised pieces per unit area of the fin varies depending on the number of the cut and raised pieces, so that the total length of the cut and raised pieces is divided into three stages.
In addition, since the standing height of the cut and raised piece 94 is constant, the ventilation resistance of the portion differs depending only on the total length of the cut and raised piece per unit area of the fin.

  The air temperature regulator 1 is required to be compact, and the space in the housing 3 is limited. For this reason, the heat exchanger 7 and the heat exchanger 9 cannot be arrange | positioned so that the distance from the sirocco fan 17 center part may become fixed. Since the distance from the center of the sirocco fan 17 is not constant, if the ventilation resistance of the heat exchanger 7 or the heat exchanger 9 is uniform, the flow velocity of the air flow passing through the heat exchanger 7 or the heat exchanger 9 is Depending on the location. Specifically, (1) the flow velocity is low in the A1 part of the heat exchanger 7, the A2 part of the heat exchanger 7, and the A3 part of the heat exchanger 9 (especially the lowest in the A2 part and A3 part near the bent part 8). ), (2) In part B of the heat exchanger 7, the flow rate is higher than in part A1, part A2, and part A3 in (1), and (3) the part C in the heat exchanger 9 has the highest flow rate.

  In the air temperature adjuster 1 of the present embodiment, if the ventilation resistance of the heat exchanger 7 or the heat exchanger 9 is uniform, the air flow rate becomes slow (the portion (1)) at the portion where the air flow velocity becomes slow. No shards are formed. Thereby, the flow velocity of the air flow passing through the heat exchanger is prevented from being cut up and further reduced by the pieces. If the ventilation resistances of the heat exchanger 7 and the heat exchanger 9 are uniform, the portion where the flow rate of the air flow is high (portion (3)) is densely cut and formed. This effectively slows down the air flow through the heat exchanger. In these intermediate portions (the portion (2)), the number of the raised and raised pieces 94 is larger than the portion (1) and smaller than the portion (3).

In the bathroom heater 1 of the present embodiment, the number of cut and raised pieces 94 formed in the heat exchangers 7 and 9 (total length of the raised and raised pieces 94 per unit area) is divided into three stages. The flow rate of the air flow passing through the heat exchangers 7 and 9 can be made uniform. Thereby, it becomes possible to improve the heat exchange performance as the whole heat exchanger to the extent expected.
Further, the ventilation resistance by the cut and raised pieces is classified only by the difference in the total length of the cut and raised pieces per unit area of the fin. For this reason, the structure of the cut-and-raised piece is simple and easy to form, and the rise in manufacturing cost is suppressed, compared with the case where the ventilation resistance is divided by the combination of the total length and the raised height of the cut-and-raised piece. Can do.

8 and 9 show comparative examples. About parts other than a heat exchanger, since there is no place different from the said Example, the same code | symbol is attached | subjected and duplication description is abbreviate | omitted. In the case of FIG. 8, since the ventilation resistance distribution of the heat exchanger itself is uniform, the ventilation resistance from the suction port to the blowout port is biased depending on the location of the heat exchanger through which the air flow passes. There is a bias in the flow velocity distribution of the air flow passing through the heat exchanger, and there is an inactive region that is not used for heat exchange. The heat exchange performance as a whole heat exchanger is reduced.
As shown in FIG. 9, there can be a technique in which the number of cut and raised pieces is different between the heat exchangers 47 and 49, but the air resistance distribution is uniform in each of the heat exchangers 47 and 49. Ventilation resistance to the outlet is biased by the location of the heat exchanger through which the air flow passes. There is a bias in the flow velocity distribution of the air flow passing through the heat exchanger, and there is an inactive region that is not used for heat exchange. The heat exchange performance as a whole heat exchanger is reduced.

FIG. 10 shows the experimental results comparing the flow velocity distribution of the air flow passing through the heat exchanger for the heat exchanger of this example and the heat exchanger of the comparative example (heat exchanger shown in FIG. 9). . Here, the vertical axis indicates the wind speed [m / s], and the horizontal axis (1) indicates the passage portion in the heat exchanger shown in FIG. 2 ((2) will be described later because it relates to the second embodiment). Yes. The flow velocity distribution of the heat exchanger of the present embodiment is indicated by a black circle graph g2, and the flow velocity distribution of the heat exchanger of FIG. 9 is indicated by a black square graph g1. The white circle graph g3 indicates the flow velocity distribution of the heat exchanger of the second embodiment, and will be described later.
The flow velocity distribution g2 of the heat exchanger of the present embodiment is uniform in comparison with the flow velocity distribution g1 of the heat exchanger of the comparative example. Therefore, it turns out that the heat exchange performance of the heat exchanger of a present Example is higher than the heat exchange performance of the conventional heat exchanger.

(Modified Example of Mounting Plate and Inner Fin) Next, a modified example of the mounting plate and the inner fin will be described with reference to FIG.
FIG. 5 illustrates one of the inner fins of the heat exchanger. Since the mounting plate is also deformed in the same manner as this fin, the description of the mounting plate is omitted in the description of this fin.
In addition to the plurality of through holes 103 and the plurality of cut and raised pieces 104, the inner fin 101 is provided with a plurality of cuts 106.
The temperature of the cooling medium flowing in the heat medium pipe 105 below (downstream) from the notch 106 is different from the temperature of the cooling medium flowing in the heat medium pipe 105 above (upstream) of the notch 106. Since air crosses from the lower part to the upper part, for example, when heating is performed, air is often flowed from the lower part to the upper part, and hot water is often flowed from the upper heat medium pipe to the lower heat medium pipe. This is because when the air flow and the hot water flow are made to oppose each other, the average temperature difference between the air and the hot water becomes larger, and the heat exchange efficiency can be increased. However, in this case, the temperature difference between the hot water flowing through the upper heat medium pipe and the hot water flowing through the lower heat medium pipe also increases and induces heat exchange between the hot waters. Sometimes not done. That is, since the temperature transmitted from the lower heat medium pipe 105 to the fin 101 is different from the temperature transmitted from the upper heat medium pipe 105 to the fin 101, heat exchange is performed between the upper side and the lower side of the fin 101. And the heat exchange performance as the whole heat exchanger will fall.
In the fin 101, by providing the notch 106, heat exchange between the upper side and the lower side of the fin 101 is interrupted, and the heat exchange performance of the entire heat exchanger can be maintained high.

(Variation 1 of Cut and Raised Piece) Next, Variation 1 of the cut and raised piece will be described with reference to FIG.
As shown in the perspective view of FIG. 6 (1), the cut and raised piece 98 is cut and raised so as to rotate in the cut hole 99 formed in the fin surface at the central portion of the short side of the cut and raised piece 98. Has been. As shown in the sectional view of FIG. 6B, the cut and raised piece 98 has an upper portion protruding from the cut hole 99 and a lower portion indented into the cut hole 99, and the air is cut and raised. Cross the surface of 98 protrusions.
The cut and raised pieces 98 can sufficiently enhance the heat transfer performance, and can be easily formed without the need to punch out the fin surfaces simply by rotating the cut and raised pieces 98 in the cut holes 99.

(Modified example 2 of cut and raised pieces) In the modified example 2 of cut and raised pieces, the standing height of each cut and raised piece is not constant. In relation to the flow velocity of the air passing through the heat exchanger, the height of the cut piece is raised at the part where the ventilation resistance is to be increased, and the height of the cut piece is lowered at the part where the ventilation resistance is to be lowered. To do. Depending on the combination of the raised height of the cut and raised piece and the total length of the cut and raised piece per unit area of the fin, the draft resistance by the cut and raised piece is divided into three or more stages.
In this way, it is possible to cope with a case where the desired number of sections cannot be accommodated only by the total length of the cut and raised pieces per unit area of the fin.

(Second Embodiment) Next, a second embodiment of an air temperature regulator embodying the present invention will be described.
FIG. 7 is a side sectional view schematically showing the ceiling-embedded air temperature controller 21 of the present embodiment. Here, differences from the air temperature adjuster 1 of the first embodiment will be mainly described, and the same components are denoted by the same reference numerals and description thereof is omitted. In FIG. 7 as well, parts of a normal ceiling-embedded air temperature controller are omitted as appropriate.
In the air temperature adjuster 21 of FIG. 7, in the heat exchanger 27 and the heat exchanger 29, the number of cut and raised pieces formed in a section sandwiched between adjacent through holes is the same as that of the first embodiment. It is different from the air temperature adjuster 1. Specifically, (1) D1 part and D2 part of the heat exchanger 27 and D3 part of the heat exchanger 29 have no cut and raised pieces, and (2) E1 part of the heat exchanger 27 And E2 part, one cut and raised piece is formed, (3) two cut and raised pieces are formed as a set in F part of the heat exchanger 27, and (4) the heat exchanger 29 Four cut and raised pieces are formed as one set in the G portion, and (5) five cut and raised pieces are formed as one set in the H portion of the heat exchanger 29. That is, the number of cut and raised pieces is divided into five stages (1) to (5). If the ventilation resistance of the heat exchanger 7 or the heat exchanger 9 is uniform, the heat exchanger 27 or the heat exchange The flow rate of the air flow passing through the vessel 29 varies depending on the location. In the part (1) where the cut and raised pieces are not formed, the flow velocity is the lowest, and in the part (2) where one cut and raised piece is formed, the flow velocity is higher than the part (1), In the part (3) in which the cut and raised pieces are formed as a set, the flow velocity is higher than in the part (2), and in the part (4) in which the four cut and raised pieces are formed as a set ( The flow velocity is higher than that in the portion 3), and the flow velocity is highest in the portion (5) in which five cut and raised pieces are formed as a set.
In the air temperature adjuster of the present embodiment, when the ventilation resistance of the heat exchanger is uniform, finely corresponding to the difference in the flow velocity of the air flow passing through the heat exchanger, By changing the number, the flow rate of the air flow passing through the heat exchanger is made more uniform. As a result, improvement in heat exchange performance is further promoted.

The flow rate distribution of the heat exchanger of the present embodiment is shown in FIG. (2) on the horizontal axis shows the passage portion in the heat exchanger shown in FIG. 7, and the white circle mark g3 shows the flow velocity distribution in the heat exchanger of this embodiment.
The flow velocity distribution g3 in the heat exchanger of the present embodiment is made more uniform than the flow velocity distribution g1 in the conventional heat exchanger and the flow velocity distribution g2 in the heat exchanger of the first embodiment. Therefore, it turns out that the heat exchange performance of the heat exchanger of a present Example is improving further.

(3rd Example) FIG. 11: is an external view of the wall-hanging type bathroom heating apparatus 51 of 3rd Example. An air inlet 61 is formed on the upper surface of the housing 53 of the bathroom heating device 51, and an air outlet 65 is formed on the lower surface of the housing 53.

FIG. 12 shows a cross-sectional view taken along the line XII-XII of the bathroom heating device 51 of FIG. In FIG. 12, the parts related to the present invention are mainly shown, and the parts of a normal wall-mounted bathroom heating device are omitted as appropriate.
The bathroom heating device 51 incorporates a heat exchanger 57, a heat exchanger 59, and a sirocco fan 67 inside the partition plate 55 of the housing 53 (in this figure, the cut and raised formed in the heat exchanger). The piece is omitted.)
The heat exchanger 57 and the heat exchanger 59 constitute a part of a polygon surrounding the sirocco fan 17 when observed from the axial direction of the substantially cylindrical sirocco fan 17. The heat exchanger is divided into a plurality of flat portions 57 and 59 and is bent at a bending portion 58 to form a substantially V shape. The heat exchanger 57 is arranged in a substantially horizontal position below the air suction port 61 so that the longitudinal direction faces the air suction port 61, and the right short side is in contact with the partition plate 55. The heat exchanger 59 is arranged substantially vertically on the rear side of the housing 3 so that the longitudinal direction is along the front surface of the housing 3. The sirocco fan 67 has a substantially cylindrical outer shape, is disposed on the lower side of the heat exchanger 57 and on the rear side of the heat exchanger 59, and blows an air flow to the air outlet 65. The air sucked from the air suction port 61 by the sirocco fan 67 passes through the heat exchanger 57 or the heat exchanger 59 and is heated and heated, and then blown out from the air outlet 65 by the sirocco fan 67. .

The heat exchangers 57 and 59 of the present embodiment have the same configuration as the heat exchangers 7 and 9 (see FIG. 2) of the first embodiment. Or it is good also as a structure similar to the heat exchangers 27 and 29 (refer FIG. 7) of 2nd Example.
In this case, as shown in FIG. 5, the fin may be provided with a heat-cutting cut, or as shown in FIG. 6, the piece is cut and raised so as to rotate in the cut hole at the center of the short side. May be. Or you may comprise so that the standing height of a cut-and-raised piece may differ.

  Also in this embodiment, the ventilation resistance by the cut and raised pieces formed on the fin is divided into three or more stages, so that the heat exchange performance as a whole heat exchanger can be exhibited at a high level, and the air temperature The performance as a coordinator will be improved.

Specific examples of the present invention have been described in detail above, but these are merely examples and do not limit the scope of the claims. The technology described in the claims includes various modifications and changes of the specific examples illustrated above.
In addition, the technical elements described in the present specification or the drawings exhibit technical usefulness alone or in various combinations, and are not limited to the combinations described in the claims at the time of filing. In addition, the technology illustrated in the present specification or the drawings achieves a plurality of objects at the same time, and has technical utility by achieving one of the objects.

The external view of the bathroom heating apparatus of 1st Example. Sectional drawing of the bathroom heating apparatus of 1st Example. The figure which shows the heat exchanger of 1st Example. The figure which shows the cut-and-raised piece of 1st Example. The figure which shows the modification of a fin. The figure which shows the modification of a cut and raised piece. Sectional drawing of the bathroom heating apparatus of 2nd Example. The figure which shows a comparative example. The figure which shows a comparative example. The figure which shows the experimental result which compared the flow velocity distribution of the airflow. The external view of the bathroom heating apparatus of 3rd Example. Sectional drawing of the bathroom heating apparatus of 3rd Example.

Explanation of symbols

1: Bathroom heating device,
3: Housing,
5: partition plate,
7, 9: heat exchanger,
11: Air inlet,
13: Partition plate,
15: Air outlet
17: Sirocco fans

Claims (2)

A housing having an air inlet and an air outlet, a blower fan accommodated in the housing, and a heat exchanger arranged at a position where an air flow flowing through the housing from the air inlet to the air outlet crosses the housing. With
The heat exchanger includes a plurality of fins arranged in parallel at intervals, and a heat medium pipe penetrating each fin in a substantially right angle direction at a plurality of positions of each fin,
Each fin is formed with a plurality of cut and raised pieces extending in the direction crossing the air flow, determined by the combination of the total length of the cut and raised pieces per unit area of the fin and the raised height of the cut and raised pieces The air temperature adjusting machine is characterized in that the ventilation resistance due to the cut and raised piece is divided into three or more stages in the whole heat exchanger in such a relationship that it is lower as it is farther from the blower fan. The heat exchanger is divided into a plurality of plane portions so as to constitute a part of a polygon surrounding the blower fan when observed from the axial direction of the blower fan having a substantially cylindrical outer shape,
There are three stages in the entire heat exchanger, in which the draft resistance determined by the combination of the total length of the cut and raised pieces per unit area of the fin and the raised height of the cut and raised pieces is lower as it approaches the vertex of the polygon. The air temperature adjuster according to claim 1, wherein the air temperature adjuster is divided as described above.

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