JPS58138994A - Heat exchanger - Google Patents

Abstract

PURPOSE:To make the fin tube type heat exchanger small-sized and compact by a method wherein rifts are formed in a fin at positions among adjoining tube passing throughholes of the fin and the intervals among the tubes are nearrowed. CONSTITUTION:The rifts 12 are formed among the tube passing throughholes 11 of the fin 1. Each of the rifts 12 is formed at a position half the shortest distance L between each two adjoining throuhghholes 11 so as to extend normal to a line connecting the centers of the throughholes 11. The length of the rift 12 is made as large as possible. For example, it is desirable that each of the vertical or longitudinal rows of the rifts 12 occupy more than two-thirds of the space where they are formed and the part of the space having no rift therein occupy less than one-thirds of the space. As a consequence, the flow of heat through the fin 1 is interrupted by the rifts 12 and the effect of the heat from the first row of the tubes 31 upon the second row of the tubes 32 is reduced sharply so that even when the intervals among the tubes are narrowed, the radiation of heat from the low temperature side tubes is not obstructed by the conduction of heat from the high temperature side tubes and the body of the heat exchanger can be miniaturized without lowering the heat exchange efficiency thereof.

Description

DETAILED DESCRIPTION OF THE INVENTION In particular, the present invention relates to a heat exchanger that requires miniaturization of equipment, such as a condenser or hot water heater for a vehicle air conditioner.

For example, a fin-tube heat exchanger has a large number of fins 1 arranged at predetermined intervals as shown in FIGS. The structure is such that a zigzag-shaped refrigerant (or hot water) passage is formed from an inlet a to an outlet b by connecting the tips of the U-bend tubes 3 with a U-bend joint 4.

In such a heat exchanger, when trying to downsize the heat exchanger, it is natural to narrow the intervals between the pend tube penetration holes formed in the fins 1, to shorten the tube intervals, and to reduce the distance between the fins 1. It is also necessary to make the interval between them as narrow as possible.

However, when the tube spacing is narrowed, there is a Fi temperature difference between the refrigerant (or hot water) flowing in adjacent tubes, so the heat transferred from the upstream tube (i.e. the high temperature tube) to the fins is transferred to the cooling air. If the heat is transferred to the tubes on the downstream side (that is, the tubes on the low temperature side) before being radiated, and it adversely affects the heat exchange of the refrigerant (or hot water), a blinding problem will occur.

In order to solve this problem, as shown in FIG. The height of the protruding pieces 6, 7.8 is gradually increased toward the later stages in the direction of the cooling air, so that the edges of all the protrusions 6, 7.8 effectively exhibit a cooling edge effect against the flow of the cooling air, and the edges of the protrusions 6, 7. A type of heat exchanger designed to improve the heat transfer coefficient has already been developed (see % Kosho No. 55-8759).

However, in the above-mentioned conventional type, although the heat dissipation of one fin can certainly be improved by using the protrusions 6, 7, and 8, the height dimension of the protrusion 8, which is the tallest of the protrusions protruding from the fin surface, is Since the spacing between the fins must be determined based on the standard, the number of fins per unit length is reduced, making it difficult to make the heat exchanger smaller and more compact. If a plurality of protrusions are to be provided in parallel in the cooling air flow direction between the service spaces, protrusions can be formed between the tube penetration spaces that are adjacent in the vertical and horizontal directions, as shown in Figure i@5. However, it is not possible to form a protrusion between diagonally adjacent tubes [4 holes], and heat is transferred from the upstream side to the downstream side through the fins between the diagonally adjacent tubes. If you put it away, there will be a hundred drawbacks.

Furthermore, the protrusions improve the heat dissipation effect by creating turbulent flow perpendicular to the air flow, but on the other hand, the turbulent flow causes
Not only does the ventilation resistance increase, but also noise is generated at relatively low wind speeds, and dirt and dust such as lint easily gets caught on the protrusions, making it difficult to remove them. When constructed by press molding, if cracks or the like occur, the ventilation space is blocked by them, resulting in problems in production, such as not being able to achieve the desired effect.

The present invention solves all of the conventional problems such as 01 above.
In other words, in the present invention, as shown in FIG. be.

The cut 12 is provided approximately in the middle of the shortest distance between adjacent holes 11 so as to be approximately perpendicular to a line connecting the centers of each hole 11.

The cross-sectional shape of the cut 12 may be a shape in which the cut end faces meet with some deviation as shown in FIG. As shown in the figure (←), it is also possible to have a shape in which the cut end faces almost completely meet and form a nearly flush surface for the entire fin (such a shape can be created by making incisions with a press and then performing roll forming to correct the misalignment). Also, the fifth
It is also possible to form a slit shape (formed by punching with a press) with a gap between the end faces of the cut as shown in Fig. f→.

Note that the length of the cut 12 is as long as possible, for example, the length of the cut 12 is as long as possible.
It is preferable that the length of the cut 12 is at least ⅔ or more, and the portion without cuts is 175 or less.

In Fig. 4, the tube penetration holes 11 are arranged in a staggered manner, and the fluid that enters directly as indicated by the arrow a flows downward through the tubes 3I in the first row, flows upward through the tubes 3I in the second row, and flows upward through the tubes 3I in the second row.
An example is shown in which the present invention is applied to a structure in which the tubes 3 in the row flow out downward and the tubes 34 in the fourth row flow upward as shown by the arrows. In this case, the tubes in each row For example, there is a very large temperature difference between the fluid flowing through the fluid flowing through the tubes 31 in the first row and the upper part of the tubes 32 in the second row. The heat of the high-temperature fluid in the second tube 31 is transmitted within the fin 1 to the low-temperature second row tubes 3 across the gap,
Although the heat dissipation of the second row tube 3 is hindered, in the present invention, the cut 12 is provided at the center of the interval, so the fin 1
The heat flow inside the second row tube 3! is divided by the cut 12! The thermal influence from the first row of tubes has been significantly reduced, and even if the tube spacing is shortened, heat dissipation from the low-temperature side tubes is no longer hindered by heat conduction from the high-temperature side tubes, and heat exchange is improved. This allows the heat exchanger main body to be made smaller without reducing efficiency.

From the perspective of achieving the object of the present invention, which is to provide cuts 12 in the fins 1 to divide the flow of heat within the fins 1 and prevent heat conduction from the high-temperature side to the low-temperature side, Fig. 5 (4)-- ,(
b)j(/→), but considering the fact that the flow resistance of the cooling air passing between the fins 1 can be reduced and the heat dissipation area of the fins 1 is free from vegetation, the 5th structure is the same.
The shape of the stem) is the most beautiful.

FIG. 4 shows an example in which the tube penetration holes 11 of the fin 1 are provided in a staggered manner.
In the case of a lattice-like arrangement, cuts 12 may be provided as shown in FIG.

Further, FIG. 17 shows an example in which the present invention is applied to a tube array in a single row, and FIG. 8 shows an example in which the present invention is applied to a tube arrangement in a single row, and FIG.

In Fig. 8, the difference in temperature between each row, that is, in the lateral direction [9I, between the adjacent tubes is not very large, so the cut 1
2 may be provided only between vertically adjacent tubes.

@9 Figure is a diagram showing an application example of the present invention, and particularly shows an example in which the present invention is applied to a condenser that condenses refrigerant.

That is, there is a counter-flow section A in which high-temperature refrigerant gas is introduced from the downstream inlet α in the cooling air inflow direction X, and the refrigerant flows in opposition to the cooling air flow; There is a cross-flow section B in which the cooling air, which is a refrigerant, flows in a direction perpendicular to the inflow direction Combining the counterflow section C that is used from the outlet,
In a heat exchanger that is capable of efficiently supercooling a refrigerant, the cut 12 is formed between each tube penetration hole 11 of the fin 1, thereby reducing the distance between each tube and deteriorating the heat exchange efficiency. heat exchanger body without
1 can be made smaller.

In this case, in each section of A, B, and C, section A and section C
There is only a temperature difference between adjacent tubes in the cooling air flow direction in the section, and there is almost no temperature difference between the tubes that blink in the direction perpendicular to the air flow in the A and C sections.
In addition, in section B, heat is released due to the liquefaction M heat of the saturated refrigerant, so the temperature remains almost constant.
As shown in Figure 0, a configuration in which the cuts 12 are provided only between the sections A, B, and C and between the tubes adjacent in the cooling air flow direction in sections A and C is sufficient to achieve the intended purpose. It can be achieved.

In addition, in Figures 9 and 10, there are cases in which the sections A, B, and C are not integrated, but instead have a structure in which each section has independent fins and only the side plates are combined as one, and in this case, the section 10.
It goes without saying that the cuts provided at the dividing portions of each section in the figure are unnecessary. Also, like this, each section A, B, C
In the case where the refrigerant refrigerant is constructed of independent fins, a liquid receiver or a liquid reservoir for gas-liquid separation may be provided in the communication passage from B to C, and only liquid refrigerant may be allowed to flow into section C.

As described above, according to the present invention, in a fin-tube heat exchanger, heat conduction within the fins between tubes having a temperature difference is achieved by using an extremely simple configuration in which only cuts are made between adjacent tube penetration holes of the fins. This not only reduces the spacing between each tube, but also reduces the spacing between the fins as there is almost no need to form any protrusions on the fins, resulting in a significantly smaller heat exchanger as a whole. It is possible to make it more compact, there is less air flow resistance, the power of the blower, etc. is small, it is easy to form cuts, and the fins are easy to form.
It is easy to handle, and it is applicable to all commonly used flow path types such as counterflow type, hairpin type, and straight type. This can bring about the following effects.

[Brief explanation of the drawing]

@ Figures 1 and 2 are a perspective view and a front view showing a general fin-tube heat exchanger, and Figures 6 (a) and (b) ti are prior art lk (Japanese Patent Publication No. 55-8759) to the present invention. These are a front view, a bottom view, and a side view of the fin of the publication. Fourth
The figure is a front view of a fin showing one embodiment of the present invention, FIG.
) ←) f-+ is a Mizuko cross-sectional view of a specific structural example of the cut 0 part in Figure 4, $1! [1,87m, Figure s, Figure 9, and Figure *1o are front views of fins showing other embodiments of the present invention, respectively. 1...Fin, 11...Tube 1 common hole, 12.
... cut, 2 ... side plate, 3 ... U bend tube, 4 ... U bend joint. (XJ 73 Figure 4 Figure 25 Figure 24 Figure procedure amendment 1. Indication of the case 1982 Patent application No. 022241 2, Title of invention heat exchanger 3, Person making the amendment Case) Relationship: Applicant: Fujiji Eukogyo (534) Fujisou Kogyo Co., Ltd. 4, Agent 5, Date of amendment order: 1939, Month, Day, Claims: A large number of 71y having multiple tube penetration holes arranged at predetermined intervals. In a fin-tube heat exchanger in which a fluid passage is formed by passing a plurality of tubes through the tube penetration holes, the centers of both tube penetration holes are connected to the tube penetration holes adjacent to each other in the age fins. A heat exchanger having a special ridge having a structure in which cuts are provided so as to be perpendicular to each other, and the cuts divide the heat conduction within the fins of the tubes passing through the tubes.

Claims (1)

[Claims] In a fin-tube heat exchanger in which a large number of fins each having a large number of tube penetration holes are arranged at predetermined intervals and a plurality of tubes are passed through the tube penetration holes to form a fluid passage, the fins have adjacent tube penetrations. A heat exchanger characterized by having a structure in which a cut is provided between the two tubes so as to be substantially perpendicular to a line connecting the centers of the two tubes, and the cut cuts off internal heat conduction between the two tubes.