JP2003262485A - Fin tube type heat exchanger, method of manufacturing the same, and refrigeration and air conditioning system - Google Patents

Abstract

(57) [Summary] [PROBLEMS] In a fin tube type heat exchanger having cut-and-raised slits, the slit dimensions and the distance between the slits have not been studied, and the heat exchange ability has not been sufficiently exhibited. SOLUTION: A plurality of plate-shaped fins 1 are arranged in parallel, through which air flows, and each of the plate-shaped fins 1 penetrates the plate-shaped fin 1 at a right angle, a working fluid flows through the inside thereof, and a direction perpendicular to the air passing direction is provided. Flat heat transfer tubes 2 provided in a plurality of stages in a row direction and provided in a plurality of rows in a row direction of an air passage direction, and cut-and-raised portions provided on a plate-shaped fin 1 surface and having openings opposed to the flow of air. This is a fin tube type heat exchanger provided with a slit 3, wherein the ratio of the width a of the cut and raised slit 3 to the distance b between the cut and raised slits 3 is 1 ≦ b / a ≦ 4.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fin tube type heat exchanger for exchanging heat between a refrigerant and a fluid such as air, a method for manufacturing the same, and a refrigerating air conditioner using the same.

[0002]

2. Description of the Related Art A conventional plate fin type heat exchanger will be described with reference to FIGS. 23 and 2
4 is a partial external view showing a plate fin type heat exchanger having a flat heat transfer tube used in the refrigerating and air-conditioning apparatus disclosed in Japanese Patent Laid-Open No. 3-128167. This heat exchanger is generally called a plate fin tube type, and is arranged at regular intervals, the plate-like fins 1 through which air flows, and the plate-like fins 1 are inserted at right angles, and the refrigerant flows inside. The heat transfer tube 2 consists of a flat heat transfer tube 2.
A group of slits is provided on the surface of the plate-shaped fin 1 in the step direction (the direction perpendicular to the direction in which air passes). The slit group is positioned such that the side ends of the slits 3 face the wind direction, and is further arranged at an angle with respect to the wind direction. By doing so, the effect of renewing the velocity boundary layer and the temperature boundary layer of the air flow at the side end portion can be expected, heat transfer is promoted, and heat exchange capacity is increased.

Further, as shown in FIGS. 23 and 24, by using the flat heat transfer tube 2 as the heat transfer tube 2,
7 is a circular heat transfer tube (FIG. 27 (a) is a plan sectional view of a heat exchanger of the circular heat transfer tube, and FIG. 27 (b) is a sectional view showing plate-shaped fins and slits). In comparison, there is an advantage that the ventilation resistance can be significantly reduced.

In order to manufacture a heat exchanger using such a flat heat transfer tube 2, in the case of the heat exchanger shown in FIG. 23, as shown in FIG. 25, a large number of layers are stacked at appropriate intervals. The plate fins 1 thus obtained are fixed with a jig, and the heat transfer tubes 2 are inserted into the insertion holes 11 of each plate fin 1 to bring the plate fins 1 and the flat heat transfer tubes 2 into close contact with each other. , Are adhered by an adhesive.

Further, in the heat exchanger shown in FIG. 24, the plate-shaped fins 1 are divided into two in the direction of the heat transfer tubes 2 arranged in a row, the divided plate-shaped fins 1 on one side are laminated, and the divided insertion holes 11 are formed. Insert the heat transfer tube 2 into the heat transfer tube 2 and then the laminated split plate fin 1 on the other side.
To unite.

[0006]

These heat exchangers have the following problems.
Although the plate-shaped fins 1 have slits 3 for promoting heat transfer, no special consideration has been made regarding the slit size, the distance between the slits, and the like. Therefore, the improvement of the heat exchange capacity is not always fully exerted.

Further, in the heat exchanger of FIG.
When the flat heat transfer tube 2 is inserted into the insertion hole 11 of the plate fin 1 as shown in FIG. 5, the plate fin 1 may be bent due to friction as shown in FIG.
There is a problem in that the intervals between the plate-shaped fins 1 become non-uniform, which not only makes the appearance of the heat exchanger unfavorable but also increases ventilation resistance. Therefore, the insertion hole 1 of the plate fin 1
Inserting the flat-shaped heat transfer tube 2 in 1 requires high precision and skill, requires labor and time for assembly, and causes a problem of increased manufacturing cost. Further, the assembly of the heat exchanger of FIG. 24 is limited to the heat transfer tube 2 having one row.

When the heat exchanger is used as the evaporator, the condensed water does not easily flow down on the plate fins 1,
When the blower is located below the heat exchanger in the weight direction, there is a problem that the blower tends to flow into the blower.

The present invention has been made in view of the above, and an object thereof is to obtain a fin-tube type heat exchanger having a large heat transfer amount, a small ventilation resistance, and a large heat exchange capacity. Another object of the present invention is to obtain a fin-tube type heat exchanger that is easy to assemble. Another object of the present invention is to obtain a fin tube type heat exchanger having good drainage of condensed water when used as a heat exchanger of an evaporator. Another object of the present invention is to obtain a fin-tube type heat exchanger having good heat transfer characteristics and good adhesion between the heat transfer tube and the plate-shaped fin. Moreover, it aims at obtaining the manufacturing method of the fin-tube type heat exchanger which is easy to assemble. Another object of the present invention is to obtain a refrigerating air conditioner using the fin tube heat exchanger or the fin tube heat exchanger manufactured by the manufacturing method.

[0010]

According to a first aspect of the present invention, there is provided a fin tube type heat exchanger in which a plurality of plate-shaped fins stacked at a predetermined interval and the plate-shaped fin are penetrated in the stacking direction. , A plurality of heat transfer tubes having a flat cross section through which the heat exchanged fluid flows and the heat exchanged fluid flows inside,
A fin tube provided with a plurality of cut-and-raised slits provided in the plate-shaped fin, and allowing the heat exchange fluid to flow between the plate-shaped fins and between the heat transfer tubes to exchange heat between the heat exchanged fluid and the heat exchange fluid. In the type heat exchanger, the heat transfer tube is
There are one or more arrays of through heat transfer tubes that are arranged so that the major axis diameter of the flat cross section matches the flow direction of the heat exchange fluid and that penetrate the plate fins in the direction perpendicular to the flow direction of the heat exchange fluid. The cut-and-raised slits provided on the fins are arranged parallel to the flow direction of the heat exchange fluid between the heat-transfer tubes of the vertically arranged heat-transfer tubes. When the distance is b, there is a relationship of 1 ≦ b / a ≦ 4.

A fin-tube heat exchanger according to a second aspect of the present invention is the fin-tube heat exchanger according to the first aspect, wherein the cut and raised slits have the same width.

A fin-tube heat exchanger according to a third aspect of the present invention is the fin-tube heat exchanger according to the first or second aspect, in which the cut-and-raised slits arranged parallel to the flow direction of the heat-exchange fluid. The number of 1 array is 2 or more and 6 or less.

The fin-tube heat exchanger according to claim 4 is the fin-tube heat exchanger according to any one of claims 1 to 3, wherein the fin-tube heat exchanger is arranged in a direction perpendicular to the flow direction of the heat-exchange fluid. In the arrangement direction of the through heat transfer tubes, the flat heat transfer tubes are divided so as to divide the major axis diameter of the flat cross section. When the number of through heat transfer tubes is n, the number of plate fins is n + 1. Is what is.

The fin-tube heat exchanger according to claim 5 is the fin-tube heat exchanger according to any one of claims 1 to 3, wherein the plate-shaped fins have a flat cross section of a flat heat transfer tube. At the downstream side end portion in the flow direction of the heat exchange fluid having the major axis diameter of, is divided in the arrangement direction of the through heat transfer tubes arranged in the direction perpendicular to the flow direction of the heat exchange fluid.

A fin-tube heat exchanger according to claim 6 is the fin-tube heat exchanger according to any one of claims 1 to 3, wherein the plate-shaped fins have a flat cross section of a flat heat transfer tube. The upstream end portion in the flow direction of the heat exchange fluid having the major axis diameter is divided in the arrangement direction of the through heat transfer tubes arranged in the direction perpendicular to the flow direction of the heat exchange fluid.

A fin-tube heat exchanger according to a seventh aspect is the fin-tube heat exchanger according to any one of the first to third aspects, wherein a fin collar protruding from the plate-shaped fin and the fin collar are provided. The fin collar and the insertion hole are surrounded by the fin collar and the insertion hole so that the insertion hole formed in the plate-shaped fin and the direction parallel to the flow direction of the heat exchange fluid can be arranged in parallel with the flow direction of the heat exchange fluid. A plurality of heat transfer tubes to be inserted, a fin collar-less portion is provided between the heat transfer tubes on the upstream side and the heat transfer tube on the downstream side in the flow direction of the heat exchange fluid, and the downstream end of the insertion hole. And the downstream end of the fin and the collar is opened with a curvature so that the downstream end of the plate fin expands outward.

A fin-tube heat exchanger according to an eighth aspect is the fin-tube heat exchanger according to any one of the first to seventh aspects, in which the through-hole heat transfer tubes are arranged in a direction perpendicular to the flow direction of the heat exchange fluid. If the arrangement of is not parallel to the direction of gravity and is inclined, the lower end of the through heat transfer tube is above the lower end of the plate fin located in the direction of gravity with respect to the end. Is.

A fin-tube heat exchanger according to a ninth aspect is the fin-tube heat exchanger according to any one of the first to eighth aspects, in which the heat transfer tube is formed in a plate-shaped fin and an insertion hole and The fin collar is inserted into a fin collar protruding from the plate-shaped fin around the insertion hole and is brought into contact with the fin collar through a brazing material layer.

According to a tenth aspect of the present invention, there is provided a fin tube type heat exchanger manufacturing method, wherein a plurality of plate-like fins laminated at a predetermined interval and the plate-like fins are penetrated in the laminating direction,
A plurality of heat transfer tubes having a flat cross section through which the heat exchanged fluid flows and the major axis of the flat cross section is aligned with the flow direction of the heat exchange fluid. In a method of manufacturing a fin tube type heat exchanger in which a heat exchange fluid and a heat exchange fluid are heat-exchanged by flowing a heat exchange fluid between the plate fins and between the heat transfer tubes. A step of forming a hole, a step of forming a through hole with a fin collar that has a concave portion partially, is provided with a brazing material, and is inclined and protrudes so as to narrow the opening toward the tip; Inserting the fins from the insertion hole side to the protruding fin collar side in the steps of stacking the fins with the fin collar on one side and aligning the insertion holes, and the step of inserting the heat transfer tubes into the insertion holes of the laminated plate fins. Process and heating By, in which the said plate-like fins and heat transfer tubes and a step of bonding via the fin collar.

According to the eleventh aspect of the present invention, there is provided a fin-tube heat exchanger manufacturing method, wherein a plurality of plate-shaped fins stacked at a predetermined interval and the plate-shaped fin are penetrated in the stacking direction,
A plurality of heat transfer tubes are arranged such that the heat exchanged fluid flows inside and the heat exchanged fluid has a flat cross section, and the major axis diameter of the flat cross section is aligned with the flow direction of the heat exchange fluid. In a method of manufacturing a fin tube type heat exchanger in which a heat exchange fluid and a heat exchange fluid are heat-exchanged by flowing a heat exchange fluid between the plate fins and between the heat transfer tubes, the plate fins have through holes. A step of forming
The fin collar is made to protrude, and against the flow of heat exchange fluid,
A step of forming an insertion hole having an opening opening at the downstream end of the plate fin; a step of stacking the plate fin with the fin collar on one side and aligning the insertion holes; and In the step of inserting the upstream heat transfer tube into the insertion hole, the step of inserting the upstream heat transfer tube from the opening into the insertion hole, the step of inserting the rod-shaped brazing material into the insertion hole, and the laminated plate fin In the step of inserting the heat transfer tube on the downstream side into the through hole of the step of inserting the heat transfer tube on the downstream side into the through hole from the opening, and by heating the heat transfer tube and the plate-shaped fin. And a step of joining through.

The refrigerating and air-conditioning apparatus according to claim 12 is
A refrigeration air-conditioning apparatus comprising a refrigeration cycle having a compressor, a condenser, a throttle device, and an evaporator, using a refrigerant as a heat exchange fluid, and air as a heat exchange fluid, wherein the condenser and the evaporator are: A fin-tube heat exchanger according to any one of claims 1 to 9 is used for at least one of them, or a fin-tube heat exchanger manufactured by the manufacturing method according to claim 10 or 11 is used. Is.

[0022]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiment 1. FIG. 1 shows an embodiment
FIG. 3 is a plan sectional view of the fin tube type heat exchanger of 1. Similarly, FIG. 2 is an external perspective view of the fin-tube heat exchanger. In the figure, reference numeral 1 is a plate-like fin, and a plurality of fins are laminated at a predetermined interval. Reference numeral 2 denotes a heat transfer tube through which a refrigerant, which is a heat exchange fluid, passes, and penetrates the plate fins in the stacking direction of the plate fins. That is, it penetrates the laminated plate fin 1 vertically. The cross section of the heat transfer tube 2 has a major axis diameter db and a minor axis diameter da.
Is a substantially elliptical shape, in other words, a flat shape, and the major axis diameter db of the flat cross section is parallel to the flow direction of air that is a heat exchange fluid. The arrangement of the through-hole heat transfer tubes 2 penetrating the plate-shaped fins 1 (having a shape that is long in the column direction and short in the step direction in FIG. 1) is perpendicular to the air flow direction (see FIG. 1).
There are two arrangements in the vertical direction and two arrangements in the parallel direction (arrangement in the column direction in FIG. 1). In FIG. 1, two arrangements in the vertical direction and three arrangements in the parallel direction (three rows) are shown. ing. Reference numeral 3 is a cut-and-raised slit formed in the plate-shaped fin 1, and a plurality of slits are arranged between the adjacent heat transfer tubes 2 of the vertically arranged heat transfer tubes 2 in parallel with the air flow direction. That is, a plurality of arrays are arranged from the upstream side to the downstream side with respect to the air flow. Further, 4 is a header, and 5 is a refrigerant inlet / outlet port.

In this embodiment, the fins 1 have a pitch Fp in the stacking direction of 0.0012 m and a fin thickness F.
t = 0.0001 m, the fin width in the air flow direction is L = 0.0254 m, the wind speed just before flowing into the fin 1 is Uf = 1.0 m / s, and the front wind speed Uf of the heat exchanger is Uf = 1.0 m / s. The distance Dp between the centers of the heat transfer tubes 2 adjacent to each other in the step direction is Dp = 0.0133 m, and the heat transfer tubes 2 are arranged in two rows in the row direction.
The fin collar 6 and the heat transfer tube 2 are completely joined by brazing up to the front edge portion of the fin collar 6 which will be described later.

Further, in order to maintain the pressure resistance inside the heat transfer tube 2, five partition walls are provided for each heat transfer tube 2, and the inside of the heat transfer tube 2 is divided into six chambers. In addition, the cross-sectional area of the refrigerant flow path in each chamber in the direction perpendicular to the refrigerant flow direction is the same. The major axis diameter parallel to the air flow direction is db.
= 0.008 m, the minor axis diameter orthogonal to the major axis diameter is da = 0.
The flatness is H = db / da = 4.0. Further, four slits are provided on the plate-shaped fin 1 in parallel with the air flow direction.

In the fin-tube type heat exchanger as described above, the heat transfer tube 2 is an aluminum alloy extruded frame member,
Alternatively, it is formed by processing a plate in which a brazing material is laminated on an aluminum plate into a flat shape and electric-sewn. The plate fin 1 is made of an aluminum alloy plate material.

In FIG. 1, the slit widths of the cut-and-raised slits 3 and the positional relationship between them are as follows. The four slit widths a are the same, and the slit-raised slit 3 has a slit width a1 = a2 = a3 = a4 = 0.002 m. The distance b between the slits is also the same, and b1 = b2
= B3 = 0.004m. The distance h1 from the front edge of the plate fin 1 to the front end of the slit 3 for the air flow and the distance h2 from the rear edge of the plate fin 1 to the rear end of the most downstream cut and slit 3. Is the same, h1 =
h2 = 0.0027m. It is preferable that the slit width a is constant because it is easier to form and fin formation is easier, but it is not necessary to be equal.

FIG. 3 is a partial external view showing the fin collar 6, the insertion hole 11 and the cut-and-raised slit 3 provided on the plate-shaped fin 1. The fin collar 6 projects from the plate-shaped fin 1 around the insertion hole 11. The heat transfer tube 2 is inserted into the insertion hole 11 and penetrates the plate fin 1. The cut-and-raised slits 3 are provided such that the side ends of the slits cut and raised from the plate-shaped fin 1 face the air flow, and a plurality of the cut-and-raised slits 3 are provided in parallel with the air flow direction. There is.

Plate-shaped fin 1 of fin-tube type heat exchanger
The air flowing between the heat transfer tubes 2 and the heat transfer tubes 2 is heated or cooled by exchanging heat with the plate fins 1. Figure 4
FIG. 6 is an explanatory diagram illustrating a developed state of a temperature boundary layer formed by cut and raised slits. A temperature boundary layer 30 develops on the surface of the plate fin 1 as shown in FIG. 4A, and heat transfer between the air and the plate fin 1 is performed through this temperature boundary layer 30. In general, the thinner the temperature boundary layer 30, the larger the amount of heat transfer per unit temperature difference between the air and the plate-like fin 1. As shown in FIG. 4 (b), the temperature boundary layer is formed at the upstream end of the cut and raised slit 3. Is updated, and the thickness of the temperature boundary layer 30 at the end of the cut and raised slit 3 on the upstream side in the air flow direction becomes very thin. The plate-shaped fins 1 are stacked at a pitch Fp in the stacking direction. For example, the temperature boundary layers 30 developed from the ends of the cut and raised slits 3 on the upstream side in the air flow direction are adjacent to each other in the stacking direction at the downstream position. It interferes with the temperature boundary layer 30 developed from the cut and raised slit 3. At the downstream of the position where the interference occurs, the thickness of the temperature boundary layer 30 is constant,
The heat transfer amount per unit length in the flow direction is a constant value.

On the other hand, when the thickness of the temperature boundary layer 30 is dt, the thickness dt [m] of the temperature boundary layer 30 at the distance y [m] in the flow direction from the upstream end of the cut and raised slit 3 in the air flow direction. Is represented by the following formula. dt = 5.0 × (ν × y / U) ^0.5 / Pr ^0.3 where ν is a kinematic viscosity coefficient, and ν = 0.000016 [m ² / s] in the case of air at normal temperature and normal pressure. Further, U is a free passage standard wind velocity (which is the average flow velocity of air flowing in the heat exchanger), and U = 1.31 [m / s]. Also, P
r is Prandtl number, and in the case of air at normal temperature and pressure, Pr = 0.
72.

Now, the distance Hf between the plate fins 1 is Hf = F
It is defined as p-Ft, and when the position of the cut-and-raised slit 3 in the stacking direction of the plate-shaped fins 1 is Hf / 2, heat transfer between the surface of the cut-and-raised slit 3 and air is promoted. , The thickness dt of the temperature boundary layer 30 at the downstream of the cut-and-raised slit 3, that is, at y = a is 1/2 of the interval Hf between the plate fins 1.
Must be smaller than. However, a [m] indicates the width of the cut and raised slit 3. Therefore, the width a of the cut-and-raised slit 3 is a ≦ U / ν × Pr ^0.6 × (Hf / 10) ² = 510 × U ×
Set so as to satisfy the condition of Fp ² .

In the standard use range of the heat exchanger for air conditioning,
The wind velocity on the basis of the free passage volume is U = 0.5 to 2 m / s, so that a ≦ 255 × Hf ^{2 to} 1020 × Hf ² . However, it should be noted that the unit of a and Hf are both [m] in the calculation. For example, Fp =
Hf if 0.0012m and Ft = 0.0001m
= 0.0011 m, and the range of a ≦ 0.00062 to 0.00246 m is satisfied. Even when the position of the cut-and-raised slit 3 in the stacking direction of the plate-shaped fins 1 is other than Hf / 2, if the slit width a is set according to the above concept, substantially the same effect can be obtained.

At this time, the heat transfer coefficient αs [W / m ² K] representing the amount of heat transfer per unit area per unit area of the surface of the cut and raised slit 3 is given as follows. That is, αs = K / a × 0.664 × Rea ^0.5 × Pr ^0.3 where K is the thermal conductivity of air and Pr is the Prandtl number, and K = 0.0261 [W
/ MK] and Pr = 0.72 [-]. Also, Rea
Is the Reynolds number and is defined as Rea = U × a / ν Therefore, by substituting αs = 3.914 × (U / a) ^0.5 a ≦ 510 × U × Hf ² , αs ≧ 0.173 / Hf

On the other hand, the heat transfer coefficient αb [W / m ² K] of the flat fin without the cut-and-raised slit 3 can be calculated as follows. αb = k / (Hf × 2) × 4.3 Therefore, αb = 0.056 / Hf Now, cut and raised on the plane of the plate fin 1 having the width L of the plate fin 1 along the air flow direction. Assuming that the number of slits 3 is N, the effective heat transfer coefficient αeff (heat transfer coefficient on the air side excluding fin efficiency Φ, and αo described later has a relationship of αo = Φ × αeff) is the above two heat transfer coefficients. Area weighted average of.
That is, αeff = αb + (N × e / L) × (αs−αb) = 0.056 / Hf × {1 + N × (1274 × U × Hf ² / L)} Therefore, αeff increases as N increases.

On the other hand, in order to give the optimum value of the number N of the cut and raised slits 3, the relationship between the ventilation resistance and N will be described. If the number N of cut-and-raised slits 3 along the air flow direction is large, the amount of heat transfer increases due to the effect of updating the temperature boundary layer 30, but the ventilation resistance of the heat exchanger increases and the driving force of the blower increases. Since Pf becomes large, it is necessary to limit the number N. Now, the pressure loss (ventilation resistance) ΔPb per unit length between the plate-shaped fins 1 without the cut-and-raised slits 3 is given as follows. ΔPb = 32 / Refp × (1 / Hf) × 1/2 × (γ
/ G) × U ² where Refp is defined as follows. Refp = U × (2 × Hf) / ν Further, γ is a specific weight [N / m ³ ] of air at normal temperature and normal pressure, and g is a gravitational acceleration [m / s ² ].

On the other hand, the pressure loss (ventilation resistance) ΔPs per unit length of the cut-and-raised slit 3 portion is generally ΔPs = 2 × 1.328 / Rea ^0.5 × (1 / Hf) ×
1/2 × (γ / g) × U ² Therefore, the sum ΔP of pressure loss (ventilation resistance) is ΔP = {(L−N × a) × 32 / Refp × (1 / H
f) + N × a × 2.656 / Rea ^0.5 × (1 / Hf)}
× 1/2 × (γ / g) × U ² = L × ΔPb + N × a ×
(ΔPs−ΔPb) Therefore, it means that the ventilation resistance ΔP increases in proportion to the number N of the cut and raised slits 3. Therefore, the heat exchange capacity E per unit length is calculated while keeping the blower driving force Pf constant.

Further, in order to reduce the driving force of the blower when the heat exchanger of this embodiment is used in a refrigerating and air-conditioning apparatus, the driving force of the blower is added to the performance evaluation items of the fin tube type heat exchanger. The driving force Pf [W] of the blower is
It is defined by the following formula. Pf = ΔP × Q where Q is the air flow rate [kg / s] passing through the heat exchanger, the length of the heat transfer tube 2 in the longitudinal direction is W [m], and the heat transfer tube 2 is
When the number of stages (number in the stage direction) of D is Dn, there is the following relationship with the front wind velocity Uf [m / s] of the heat exchanger. Uf = Q / ρ / (W × Dp × Dn)

Hereinafter, α and ΔP are calculated using the width a of the cut and raised slit 3 and the distance b between the slits as parameters,
The air flow rate Q was determined under the condition that the driving force Pf of the blower was constant, and the heat exchange capacity E of the heat exchanger at this time was calculated. The slit shape and arrangement are constant. Further, the heat exchange capacity E is evaluated by the heat exchange amount E [W / K] per unit temperature, and is calculated by the following equation. E = Q × H × ε ε = 1−exp (−T) T = Ao × K / (Q × H) K = 1 / (1 / αo + Ao / Ai / αi + Ac / Ai /
.alpha.c) Here, H [W / kg · K ] is air specific heat, epsilon temperature ^{efficiency, K [W / m 2 K} ] is the thermal transfer ^{coefficient, αo [W / m 2 K} ] and αi [W / m ² K] is the heat transfer coefficient outside the tube and the heat transfer coefficient inside the tube, αc [W / m ² K] is the heat transfer coefficient at the contact portion between the plate fin 1 and the heat transfer tube 2, and Ao [m ² ] is the heat exchanger. Air side total heat transfer area, Ap [m ² ] is air side pipe heat transfer area of heat exchanger, Af [m ² ] is air side fin heat transfer area of heat exchanger, Ai [m ² ] is heat exchange Heat transfer area on the refrigerant side of the vessel, A
c [m ² ] is the contact area of the plate-shaped fin 1 and the heat transfer tube 2, and the parameter depending on the shape of the heat exchanger, the heat exchange capacity E is the step pitch Dp, the fin width L, the pitch Fp, the plate-shaped fin. It is a value that can be calculated if the thickness Ft of 1 and the contact heat transfer coefficient αc between the plate-shaped fin 1 and the heat transfer tube 2 are determined.

The relationship between the shape parameter and the heat exchange capacity E is shown in FIGS. 5 and 6 below. In these figures, the heat exchange capacity E [W / K] is a value when the number of stages of the heat transfer tube 2 is one and the length W in the longitudinal direction of the heat transfer tube 2 is a unit length.

FIG. 5 is a cut-and-raised slit 3 for the fin-tube type heat exchanger of the flat heat transfer tube 2 of the present embodiment and the fin-tube type heat exchanger of the circular heat transfer tube 2 shown in FIG. Of the slit width a and the distance b between slits b / a = 2, the driving force Pf of the blower is constant, and the heat exchange capacity per unit length in the longitudinal direction of the heat transfer tube 2 This is a calculation of E. In the heat exchanger of the circular heat transfer tube 2, the pitch Fp in the stacking direction of the plate fins 1 is Fp = 0.0012 m, the thickness Ft of the plate fins 1 is Ft = 0.0001 m, and the air flow direction is Has a plate fin width L of L = 0.0254 m, a front wind velocity Uf of the heat exchanger is Uf = 1.0 m / s, and a distance Dp between centers of heat transfer tubes adjacent to each other in the step direction of the heat exchanger is Dp = 0.254. 026
6 m, the heat transfer tubes are arranged in two rows in the row direction, and the plate-shaped fins 1 and the heat transfer tubes 2 are brought into close contact with each other by a method in which the heat transfer tubes 2 are spread by a pipe expanding rod or high-pressure water and brought into close contact with the plate fins 1.

From FIG. 5, the heat exchange capacity E takes the maximum value in the vicinity of the number N of cut and raised slits 3 = 4. This is the ventilation resistance Δ
P increases linearly when the number of slits increases, but the heat transfer amount q asymptotically approaches a constant value. Therefore, when a slit of N = 4 or more is cut and raised, the increment of the pressure loss (ventilation resistance) ΔP increases. This is because the air volume Q is smaller than the increment of q and decreases. Therefore, the cut-and-raised slit 3 is 4 in this embodiment.
Although it is desirable to set the number of heat exchangers to be 1, the heat exchange capacity E is 3% or less of the maximum value within the range of 2 to 6 and the effect is sufficiently exerted. When the heat exchanger of the circular heat transfer tube 2 and the heat exchanger of the flat heat transfer tube 2 are compared, the heat exchanger of the flat heat transfer tube 2 cuts and raises the slit 3
The maximum number of is small. This is because the heat exchanger of the flat heat transfer tube 2 has a smaller pressure loss in the heat transfer tube 2 portion, and the ratio of the pressure loss of the cut and raised slit 3 to the total pressure loss ΔP is higher. Further, the absolute value of the heat exchange capacity E of the heat exchanger of the flat heat transfer tube 2 is larger than that of the heat exchanger of the circular heat transfer tube 2 as a method of joining the plate fins 1 and the heat transfer tube 2. This is because brazing is used, and thus the contact heat transfer coefficient αc is very large.

FIG. 6 shows the fin-tube type heat exchanger of the flat heat transfer tube 2 of this embodiment and the fin-tube type heat exchanger of the circular heat transfer tube shown in FIG. With the number N as a parameter, the number of cut and raised slits 3 was set to 4, and the driving force Pf of the blower was kept constant, the heat exchange capacity E per unit length in the longitudinal direction of the heat transfer tube 2 was calculated. . The specifications of the heat exchanger for the circular heat transfer tube 2 are the same as those in FIG. 5, except for the number of cut and raised slits 3.

From FIG. 6, the heat exchange capacity E takes the maximum value in the vicinity of b / a = 2. This is because when the b / a is increased, the ventilation resistance ΔP is reduced, but the heat transfer amount q is also reduced. Therefore, b / a =
This is because when the number is 2 or more, the decrease in the heat transfer amount q is larger than the increase in the air amount Q due to the decrease in the pressure loss (ventilation resistance) ΔP. Therefore, in the present embodiment, it is desirable to set b / a = 2, but when b / a is in the range of 1 to 4, the heat exchange capacity E is within 3% of the maximum value, and a sufficient effect is obtained. Demonstrate. Further, when the heat exchanger of the circular heat transfer tube 2 and the heat exchanger of the flat heat transfer tube 2 are compared, the maximum value of b / a is smaller in the heat exchanger of the circular heat transfer tube 2. . This is because the heat exchanger of the flat heat transfer tube 2 has a smaller pressure loss at the portion of the heat transfer tube 2 and the ratio of the pressure loss of the plate fin 1 to the total pressure loss ΔP is larger. Also,
The absolute value of the heat exchange capacity E of the heat exchanger of the flat heat transfer tube 2 is larger than that of the heat exchanger of the circular heat transfer tube 2 as a method of joining the plate fin 1 and the heat transfer tube 2 to each other. This is because the contact heat transfer coefficient αc is very large. The width a of the cut and raised slit 3
With respect to the distance b between the cut and raised slits 3 and the width a of the cut and raised slits 3 and the distance b between the cut and raised slits 3 are different, the width a of the cut and raised slits 3 and the cut and raised slits 3 In the relationship shown in FIG. 1, the distance b is 1 ≦ b1
/ A1 ≦ 4, 1 ≦ b2 / a2 ≦ 4, 1 ≦ b3 / a3 ≦ 4
.. is established, the same effect as described above can be obtained.

FIG. 7 shows a fin-tube type heat exchanger in which the cut-and-raised slits 3 are formed at a constant angle with respect to the air flow, but the number of the cut-and-raised slits 3 is two.
6 and b / a are 1 to 4, the heat exchange capacity E is the largest, and the same effect as that of the cut-and-raised slit 3 shown in FIG. 3 is expected.

FIG. 8 shows an example of a fin-tube type heat exchanger in which the through heat transfer tubes 2 are arranged in one direction perpendicular to the air flow direction, that is, the heat transfer tubes 2 are arranged in one row in the step direction. Figure 1
Similar to the two-row heat exchanger shown in Fig. 2, when the number of slits 3 is 2 to 6 and b / a is 1 to 4, the heat exchange capacity E is the largest and the same effect as in Fig. 1 is obtained. Expected However, in order to maintain the pressure resistance inside the heat transfer tube 2, the number of partition walls is increased corresponding to the increase in the major axis diameter of the heat transfer tube 2.

The method of assembling the fin tube type heat exchanger of the first embodiment will be described below. FIG. 9 shows the fin-tube type heat exchanger shown in FIG. 1, in which the plate fin 1 is divided in the stepwise direction of the heat transfer tube 2 by dividing lines 7, 7.
1 shows a fin-tube heat exchanger in which the plate fins 1 are composed of three sheets 1a, 1b and 1c. That is, the plate-shaped fin 1 is divided so that the major axis diameter of the flat cross section of the flat heat transfer tube 2 is divided.

FIG. 10 shows a state of temporary assembly before brazing of the heat exchanger of FIG. In FIG. 10, 6 is a fin collar, and heat transfer tubes 2a, 2b and rod-shaped brazing materials 8a, 8b, 8c, 8d are inserted into the fin collar 6 at both ends. Since FIG. 10 is a diagram showing the temporary assembly, the divided portions 1a, 1b, 1c of the plate-shaped fin 1 are separated by the amount of the brazing materials 8a, 8b, 8c, 8d. By the brazing, the brazing materials 8a, 8b, 8c, 8d are melted out, and the plate-shaped fins 1a, 1b, 1c are moved by their own weight, and they coincide with each other at the dividing lines 7, 7 as shown in FIG. FIG. 11 is a flow chart of the method for assembling the heat exchanger of FIG. 9, and the process is fin fining (S1) (fin finning is one in which a plate-shaped fin is punched out from one plate by a die, a fin collar 6 and a cut-and-raised slit. Three
The fins 1a are laminated in the axial direction of the heat transfer tubes and fixed by a jig (S2), the brazing rod 8a is arranged below the fins 1a in the gravity direction (S3), and the heat transfer tubes 2a are gravitated by the fins 1a. Insert from the top in the direction (S4), fix the brazing rod 8b to the top of the heat transfer tube 2b in the direction of gravity (S5), stack the fins 1b in the tube axis direction, and fix them with a jig, and heat Wood rod
8B is engaged (S6), brazing rod 8c is arranged below fin 1b in the direction of gravity (S7), heat transfer tube 2b is inserted from above fin 1b in the direction of gravity (S8), brazing bar 8d is connected to heat transfer tube Fixed to the upper part of 2b (S9), fins 1c are laminated in the axial direction of the tube, and in a state of being fixed by a jig, engage with the heat transfer tube 2b and the brazing rod 8d (S10), temporary assembly of header parts (S10) Then, the steps are carried out by placing in a Nocolock continuous furnace, heating and joining (S11), coating the fin surface with a hydrophilic material coating material (S12), and drying (S13).

As described above, when brazing is performed as a method for bringing the fin collar 6 and the heat transfer tube 2 into close contact with each other, as in the conventional method shown in FIG. When the brazing material is attached to the heat transfer tube 2, it is difficult to insert the clearance because it is difficult to secure the clearance. In the case of the present embodiment, since the heat transfer tube 2 is fitted from the insertion hole 11 opened at the end of the plate fin 1, if the brazing material rods are arranged at both ends of the heat transfer tube 2, a sufficient amount of brazing material is secured. You can
Since the plate fin 1 and the brazing material can be brought into close contact with each other, the contact heat transfer coefficient αc is expected to increase to almost infinity. After brazing, the brazing material spreads between the plate-shaped fins 1 and the heat transfer tubes 2, and the heat transfer tubes 2 move to the front edge of the fin collars 6 and come into contact with the fin collars 6 without any gaps, thus providing a good-looking heat. It becomes an exchange.

Further, generally, when the number of rows of the heat transfer tubes 2 is n, by setting the number of divisions of the plate-shaped fins 1 to be n + 1, the same assembly method as in FIG. 11 can be used,
That is, it goes without saying that the number of rows of the heat transfer tubes 2 can be large, and the same effect as described above can be obtained.

FIG. 12 shows another assembly method.
The plate-shaped fins 1 are divided at the end of the heat transfer tube 2 in a stepwise direction by a dividing line 7, and the rear edge of the heat transfer tube 2 is arranged at the rear edge of the plate fin 1 in the air flow direction. 2 shows a heat exchanger according to the present invention. That is, the plate-shaped fins 1 are arranged at the downstream end portion in the flow direction of the heat exchange fluid having the major axis diameter of the flat heat transfer tube 2 in the flow direction of the heat exchange fluid so as to penetrate through the heat transfer fluid in a direction perpendicular to the flow direction of the heat exchange fluid. It consists of the ones divided in the arrangement direction of the heat tubes. In this case, the plate-shaped fin 1 is composed of two sheets 1a and 1b, the fixing jig only needs to be used twice, and the number of steps of temporary assembly in FIG. 10 is greatly reduced. In addition, the plate fins 1 and the heat transfer tubes 2
The brazing rod placed between the heat transfer tubes 2a and 2b is not attached to one of the heat transfer tubes 2a and 2b.
Insert a book. The brazing material is reduced and the cost is reduced.

FIG. 13 shows still another assembling method, in which the plate-shaped fin 1 is divided into 1a and 1b in the step direction by the dividing line 7 at the end of the heat transfer tube 2, and the plate-shaped fins are arranged in the air flow direction. 1 shows a heat exchanger in which the front edge of the heat transfer tube 2 is arranged at the front edge of 1. That is, the plate-shaped fins 1 are arranged at the upstream end of the flat heat transfer tube 2 in the flow direction of the heat exchange fluid having the major axis diameter of the flat cross section so as to be arranged in the direction perpendicular to the flow direction of the heat exchange fluid. It is composed of two elements divided in the arrangement direction. It goes without saying that the same effect as in FIG. 12 is also obtained in this case.

FIG. 14 is an example showing another assembling method, and is a view before the insertion of the heat transfer tube 2 in which the notch 6d which is a partial recess is provided on the inner surface of the fin collar 6 in the plate fin 1. FIG. 15 is a view showing a cross section taken along line AA in FIG.

FIG. 16 shows an AA cross section after the heat transfer tube 2 is inserted. A brazing material layer 9 is present between the plate fin 1 and the heat transfer tube 2, and the plate fin 1 and the heat transfer tube 2 are in close contact with each other. .

FIG. 17 is a flowchart of the method for assembling the heat exchanger of FIG. In the process, fins are removed (S1), plate fins 1 are laminated in the axial direction of the heat transfer tubes 2 and fixed with a jig (S2), and plate fins 1 are coated with a brazing material on the surface. Although it is sufficient to apply only to the portion 6 of the fin, it is difficult to apply only to the portion of the fin collar 6, so the heat transfer tube 2 is applied to the entire fin from the viewpoint of processing). Inserted (S
3), header component temporary assembly (S4), heating into a Nocolock continuous furnace (S5), hydrophilic coating material application (S6) on the surface of the plate-shaped fin 1, and drying (S7). Here, in the step of inserting (S3) the heat transfer tube 2 into the plate fin 1 from the insertion direction of the heat transfer tube 2 of the plate fin 1 (shown in FIG. 16), the brazing material is applied to the plate fin 1. In this case, the brazing material is easier to peel off than the fin collar 6. Therefore, by providing the notch 6d, which is a concave portion partially provided on the inner surface of the fin collar 6, it is possible to prevent complete peeling of the brazing material.

Further, the fin collar 6 is inclined toward the heat transfer tube 2 side with respect to the insertion direction of the heat transfer tube 2 (shown in FIG. 16).
That is, the fin collar 6 is inserted in the insertion direction of the heat transfer tube 2 at the time of inserting the heat transfer tube 2 by forming the insertion hole 11 by the fin collar 6 which is inclined and protrudes so as to narrow the opening toward the tip (shown in FIG. 15). The fin collar 6 and the heat transfer tube 2 are in contact with each other without any gap. By doing so, it is possible to prevent the bending of the plate-shaped fin 1 when the heat transfer tube 2 is inserted, as shown in FIG. 26, which occurs when the clearance between the fin collar 6 and the heat transfer tube 2 cannot be secured.

FIG. 18 shows still another assembly example, in which the plate-shaped fins 1 have the through holes 11 of the heat transfer tubes 2 opened in the direction parallel to the air flow direction and at the downstream end of the plate-shaped fins 1. To insert the upstream heat transfer tube 2 first, then insert the rod-shaped brazing material, and further insert the downstream heat transfer tube 2 through the opening. Shows a heat exchanger into which two rows of heat transfer tubes 2 are inserted. Although the fin collar 6 projects around the insertion hole 11, between the heat transfer tube 2 on the upstream side and the heat transfer tube 2 on the downstream side,
A portion without the fin collar 6 is provided when the rod-shaped brazing material is inserted. That is, here the fin collar 6 is 6
It is divided into a and 6b. The opening opening at the downstream end of the plate-shaped fin 1 has a curvature so that the downstream end of the insertion hole 11 and the downstream end of the fin collar 6b open outward. There is.

According to this assembly, a plurality of rows of the heat transfer tubes 2 can be provided without dividing the plate-shaped fin 1, and the assembling is easy. Also, the cost of the rod-shaped brazing material is reduced because the number of n-1 heat transfer tubes is required for the brazing material. Further, if the fin collar 6 is not divided, when this heat exchanger is used in an evaporator, condensed water easily stays above the fin collar 6,
Since the drainage property deteriorates, the fin collar 6 is divided between the heat transfer tubes 2 to improve the drainage property. Furthermore, in this case, since the fin collar 6b on the downstream side of the air flow is likely to fall outside the heat transfer tube 2, the fin collar 6 on the downstream side of the air flow is likely to fall.
b is provided with a radius that spreads outward. By doing so, the fin collar 6b is less likely to fall down, and the fin collar 6b and the heat transfer tube 2 are easily brought into close contact with each other.

Embodiment 2. FIG. 19: is a figure which shows the usage example of the fin tube type heat exchanger of Embodiment 2, and is an example of the heat exchanger of 1 row. One row heat exchanger and once-through fan 1
It shows a refrigerating air-conditioning system configured using 0a,
12 is a drain pan and 13 is condensed water. The heat transfer tube 2 is always installed above the plate-shaped fin 1 with respect to the direction of gravity. That is, when the arrangement of the through heat transfer tubes 2 in the direction perpendicular to the air flow direction is not parallel to the gravity direction and is inclined, the lower end of the through heat transfer tubes 2 is positioned in the gravity direction with respect to the end. It is above the lower end of the plate-shaped fin 1.

As shown in FIG. 20, the heat transfer tube 2 is provided downward in the gravity direction.
, There is no drainage for the condensate and the condensate drips downwards. Therefore, by installing the heat transfer tube 2 above the plate-shaped fins 1 with respect to the direction of gravity, a flow path of condensed water is always secured on the plate-shaped fins 1 downward in the direction of gravity, and the condensed water falls down to the blower. Never. Needless to say, the same effects as in the case of FIG. 20 are obtained in the cases of FIGS. 12 and 13 in which the heat transfer tubes 2 are arranged in two rows.

Third Embodiment FIG. 21 is a diagram showing an example of use of the fin-tube heat exchanger of the third embodiment, in which the hairpin portion is arranged at the end of the heat exchanger of the flat heat transfer tube 2 and the header 4 is arranged at the other end. When a propeller-type blower 10b is used as a refrigerating and air-conditioning apparatus, since the air volume is large, the heat exchanger is large and is often bent into an L-shape or a U-shape with respect to the axial direction of the heat transfer tube 2. Flat heat transfer tube 2
When the heat exchanger of No. 2 is used, it is difficult to bend the long axis of the flat heat transfer tube 2, and it is necessary to divide the heat transfer tube into two or three.

Fourth Embodiment FIG. 22 is a diagram showing the refrigerating and air-conditioning apparatus of the fourth embodiment. The refrigerant circuit of the refrigeration / air-conditioning system shown in the figure includes a compressor 21, a condensing heat exchanger 22, and a throttle device 2.
3, an evaporation heat exchanger 24, and a blower 10. By using the heat exchanger described in the first embodiment in the condensing heat exchanger 22 or the evaporative heat exchanger 24, or both, a refrigerating and air-conditioning apparatus with high energy efficiency can be realized. Here, the energy efficiency is defined by the following equation. Heating energy efficiency = Indoor heat exchanger (condenser) capacity / total input Cooling energy efficiency = Indoor heat exchanger (evaporator) capacity / total input

Incidentally, the above-mentioned Embodiments 1 to 4
For the heat exchanger and the refrigerating and air-conditioning apparatus using the heat exchanger described in Section 2, the HCFC (R22) and HFC (R116, R12
5, R134a, R14, R143a, R152a, R
227ea, R23, R236ea, R236fa, R
245ca, R245fa, R32, R41, RC31
8 and the like, or mixed refrigerants of several kinds of these refrigerants R407A, R407
407B, R407C, R407D, R407E, R4
10A, R410B, R404A, R507A, R50
8A, R508B, etc.), HC (butane, isobutane,
Ethane, propane, propylene, etc., mixed refrigerants of these refrigerants), natural refrigerants (air, carbon dioxide, ammonia, etc., mixed refrigerants of these refrigerants), mixed refrigerants of these refrigerants, etc. The effect can be achieved with any type of refrigerant.

Although the example of air and refrigerant has been shown as the working fluid for heat exchange, the same effect can be obtained by using other gas, liquid or gas-liquid mixed fluid.

Although the heat transfer tube 2 and the plate fin 1 are often made of different materials, copper is used for the heat transfer tube 2 and the plate fin 1, aluminum is used for the heat transfer tube 2 and the plate fin 1, and so on.
By using the same material, it becomes possible to braze the plate-shaped fin 1 and the heat transfer tube 2, the contact heat transfer coefficient between the plate-shaped fin 1 and the heat transfer tube 2 is dramatically improved, and the heat exchange capacity is significantly improved. . Also, recyclability can be improved.

As a method for bringing the heat transfer tube 2 and the plate-like fin 1 into close contact with each other, when performing brazing in the furnace, the plate-like fin 1 is used.
By applying the hydrophilic material to the above in a post-treatment, it is possible to prevent the hydrophilic material from burning off during brazing in the case of the pre-treatment.

When the pressure resistance is to be increased, measures such as increasing the wall thickness and increasing the number of partition walls inside the heat transfer tube 2 may be taken. When the thickness is increased, the outer diameter of the heat transfer tube 2 also increases, and the cost of the heat transfer tube 2 also rises. However, by adjusting the step pitch, row pitch, flatness ratio, and the number and shape of the cut and raised fins 3, the ventilation resistance can be increased. The effect of the present embodiment can be sufficiently exerted by appropriately setting these values in consideration of the balance of heat transfer promotion.

The heat exchanger and the refrigerating air-conditioning system using the heat exchanger described in the first embodiment are mineral oil-based,
Alkylbenzene oil type, ester oil type, ether oil type,
The effect of any refrigerating machine oil can be achieved regardless of whether or not the refrigerant and the oil are melted, such as a fluorinated oil system.

[0067]

The fin-tube heat exchanger according to claim 1 of the present invention has a plurality of plate-like fins laminated at a predetermined interval, and the plate-like fins penetrating in the laminating direction to cover the inside. A plurality of heat transfer tubes having a flat cross section through which the heat exchange fluid flows and the heat exchange fluid flows, and a plurality of cut-and-raised slits provided in the plate fins are provided between the plate fins and the heat transfer pipes. In the fin-tube type heat exchanger for exchanging heat between the fluid to be exchanged and the heat exchange fluid by flowing the heat exchange fluid between the heat transfer tubes, the heat transfer tubes have a flat cross-section whose major axis diameter is in the flow direction of the heat exchange fluid. Arranged to match,
There is one or more array of penetrating heat transfer tubes penetrating the plate-shaped fins in the direction perpendicular to the flow direction of the heat exchange fluid, and the cut-and-raised slits provided in the plate-shaped fins are the heat transfer tubes of the array of vertical-direction heat transfer tubes. Between the cut-and-raised slits and the width between the cut-and-raised slits is a and the distance between the cut-and-raised slits is b, there is a relation of 1 ≦ b / a ≦ 4. It is possible to obtain a fin-tube type heat exchanger having a large heat transfer amount and a small ventilation resistance, and thus a good heat exchange capacity.

Further, the fin-tube heat exchanger according to claim 2 is the fin-tube heat exchanger according to claim 1, in which all the cut and raised slits have the same width, which facilitates the formation of the plate-shaped fins. Become.

The fin-tube heat exchanger according to claim 3 is the fin-tube heat exchanger according to claim 1 or 2, wherein the cut-and-raised slits are arranged parallel to the flow direction of the heat-exchange fluid. Since the number of one array is 2 or more and 6 or less, a fin-tube heat exchanger having a large heat transfer amount and a small ventilation resistance, and thus a good heat exchange capacity can be obtained.

The fin-tube heat exchanger according to claim 4 is the fin-tube heat exchanger according to any one of claims 1 to 3, wherein the fin-tube heat exchanger is arranged in a direction perpendicular to the flow direction of the heat exchange fluid. In the arrangement direction of the through heat transfer tubes, the flat heat transfer tubes are divided so as to divide the major axis diameter of the flat cross section. When the number of through heat transfer tubes is n, the number of plate fins is n + 1. Therefore, even if the number of through-hole heat transfer tubes is plural, the fin tube heat exchanger is easy to assemble and looks good when completed.

The fin-tube heat exchanger according to claim 5 is the fin-tube heat exchanger according to any one of claims 1 to 3, wherein the plate-shaped fins are flat cross-sections of the heat transfer tubes. At the downstream end in the flow direction of the heat exchange fluid having the major axis diameter of, the heat transfer fluid is divided into the through heat transfer tubes arranged in the direction perpendicular to the flow direction of the heat exchange fluid. Even if the number of arrays is more than one, the fin tube heat exchanger can be obtained with a better assembling property and a good appearance when completed.

The fin-tube heat exchanger according to claim 6 is the fin-tube heat exchanger according to any one of claims 1 to 3, wherein the plate-shaped fins have a flat cross section of a flat heat transfer tube. At the upstream end in the flow direction of the heat exchange fluid having the major axis diameter of, the pipe is divided in the arrangement direction of the through heat transfer tubes arranged in the direction perpendicular to the flow direction of the heat exchange fluid. Even if the number of arrays is more than one, the fin tube heat exchanger can be obtained with a better assembling property and a good appearance when completed.

A fin-tube heat exchanger according to a seventh aspect is the fin-tube heat exchanger according to any of the first to third aspects, wherein the fin collar protruding from the plate-shaped fin and the fin collar. The fin collar and the insertion hole are surrounded by the fin collar and the insertion hole so that the insertion hole formed in the plate-shaped fin and the direction parallel to the flow direction of the heat exchange fluid can be arranged in parallel with the flow direction of the heat exchange fluid. A plurality of heat transfer tubes to be inserted, a fin collar-less portion is provided between the heat transfer tubes on the upstream side and the heat transfer tube on the downstream side in the flow direction of the heat exchange fluid, and the downstream end of the insertion hole. Since the downstream end of the fin portion and the fin collar has an opening with a curvature so as to spread outward at the downstream end of the plate-shaped fin, even if the number of through heat transfer tubes is multiple, the assemblability is better and evaporation is improved. Used as a heat exchanger for If you, finned tube heat exchanger that can improve drainage of the condensed water is obtained.

Further, a fin-tube heat exchanger according to an eighth aspect is the fin-tube heat exchanger according to any one of the first to seventh aspects, in which the through-hole heat transfer tubes are arranged in a direction perpendicular to the flow direction of the heat exchange fluid. If the arrangement is not parallel to the direction of gravity and is inclined, the lower end of the through heat transfer tube is above the lower end of the plate fin located in the direction of gravity with respect to the end. When used as a heat exchanger for an evaporator,
A fin-tube heat exchanger that can improve the drainage of condensed water can be obtained.

A fin-tube heat exchanger according to a ninth aspect is the fin-tube heat exchanger according to any one of the first to eighth aspects, in which the heat transfer tube is formed into a plate-shaped fin and an insertion hole and Since it was inserted into the fin collar projecting from the plate-shaped fin around the insertion hole and brought into contact with the fin collar through the layer of brazing material, high heat transfer performance with good adhesion between the heat transfer tube and the plate-shaped fin was achieved. A fin-tube type heat exchanger having is obtained.

According to a tenth aspect of the present invention, there is provided a fin tube type heat exchanger manufacturing method, wherein a plurality of plate-like fins laminated at a predetermined interval and the plate-like fins are penetrated in the laminating direction,
A plurality of heat transfer tubes having a flat cross section through which the heat exchanged fluid flows and the major axis of the flat cross section is aligned with the flow direction of the heat exchange fluid. In a method of manufacturing a fin tube type heat exchanger in which a heat exchange fluid and a heat exchange fluid are heat-exchanged by flowing a heat exchange fluid between the plate fins and between the heat transfer tubes. A step of forming a hole, a step of forming a through hole with a fin collar that has a concave portion partially, is provided with a brazing material, and is inclined and protrudes so as to narrow the opening toward the tip; Inserting the fins from the insertion hole side to the protruding fin collar side in the steps of stacking the fins with the fin collar on one side and aligning the insertion holes, and the step of inserting the heat transfer tubes into the insertion holes of the laminated plate fins. Process and heating According to the present invention, the fin tube having the step of joining the heat transfer tube and the plate-shaped fin via the fin collar has good assembling property and good heat transfer characteristics with good adhesion between the heat transfer tube and the plate-shaped fin. A mold heat exchanger can be manufactured.

According to the eleventh aspect of the present invention, in the method of manufacturing a fin-tube heat exchanger, a plurality of plate-like fins laminated at a predetermined interval and the plate-like fins are penetrated in the laminating direction,
A plurality of heat transfer tubes are arranged such that the heat exchanged fluid flows inside and the heat exchanged fluid has a flat cross section, and the major axis diameter of the flat cross section is aligned with the flow direction of the heat exchange fluid. In a method of manufacturing a fin tube type heat exchanger in which a heat exchange fluid and a heat exchange fluid are heat-exchanged by flowing a heat exchange fluid between the plate fins and between the heat transfer tubes, the plate fins have through holes. A step of forming
The fin collar is made to protrude, and against the flow of heat exchange fluid,
A step of forming an insertion hole having an opening opening at the downstream end of the plate fin; a step of stacking the plate fin with the fin collar on one side and aligning the insertion holes; and In the step of inserting the upstream heat transfer tube into the insertion hole, the step of inserting the upstream heat transfer tube from the opening into the insertion hole, the step of inserting the rod-shaped brazing material into the insertion hole, and the laminated plate fin In the step of inserting the heat transfer tube on the downstream side into the through hole of the step of inserting the heat transfer tube on the downstream side into the through hole from the opening, and by heating the heat transfer tube and the plate-shaped fin. It is possible to manufacture a fin-tube heat exchanger with good assemblability even when the number of through-hole heat transfer tubes arranged is plural.

Further, the refrigerating and air-conditioning apparatus according to claim 12 is
A refrigeration air-conditioning apparatus comprising a refrigeration cycle having a compressor, a condenser, a throttle device, and an evaporator, using a refrigerant as a heat exchange fluid, and air as a heat exchange fluid, wherein the condenser and the evaporator are: Since the fin tube type heat exchanger according to any one of claims 1 to 9 is used for at least one of them, or the fin tube type heat exchanger manufactured by the manufacturing method according to claim 10 or 11, is used. By using the fin-tube type heat exchanger having the effects described in the above claims for the condenser and the evaporator, a refrigerating and air-conditioning apparatus having the respective effects can be obtained.

[Brief description of drawings]

FIG. 1 is a plan sectional view showing a fin-tube heat exchanger according to a first embodiment of the present invention.

FIG. 2 is an external perspective view showing the fin tube heat exchanger according to the first embodiment of the present invention.

FIG. 3 is a partial external view showing a fin collar and a cut-and-raised slit of the fin-tube heat exchanger according to the first embodiment of the present invention.

FIG. 4 is an explanatory diagram showing development of a temperature boundary layer formed by cut and raised slits on plate-like fins of the fin-tube heat exchanger according to Embodiment 1 of the present invention.

FIG. 5 is a characteristic diagram showing a relationship between the number of cut and raised slits of the plate-shaped fin and the heat exchange capacity of the fin-tube heat exchanger according to the first embodiment of the present invention.

FIG. 6 is a characteristic diagram showing the relationship between the ratio b / a of the cut-and-raised slit width a and the slit-to-slit distance b of the plate-like fins of the fin-tube heat exchanger according to Embodiment 1 of the present invention, and heat exchange capacity. Is.

FIG. 7 is a partial external view showing another fin collar and a cut-and-raised slit of the fin-tube heat exchanger according to the first embodiment of the present invention.

FIG. 8 is a plan sectional view showing another fin-tube heat exchanger according to the first embodiment of the present invention.

FIG. 9 is a plan sectional view showing still another fin-tube heat exchanger according to the first embodiment of the present invention.

FIG. 10 is an explanatory view illustrating an assembly process of the fin tube type heat exchanger shown in FIG. 9 of the present invention.

FIG. 11 is a flowchart showing an assembly process of the fin-tube heat exchanger shown in FIG. 9 of the present invention.

FIG. 12 is a plan sectional view showing still another fin-tube heat exchanger according to the first embodiment of the present invention.

FIG. 13 is a plan sectional view showing still another fin-tube heat exchanger according to the first embodiment of the present invention.

FIG. 14 is a plan cross-sectional view showing still another fin-tube heat exchanger according to the first embodiment of the present invention.

15 is a partial cross-sectional view showing a plate-shaped fin and a fin collar of the fin-tube type heat exchanger shown in FIG. 14 of the present invention.

16 is a partial cross-sectional view showing a state in which a heat transfer tube is inserted into the fin collar of the fin-tube heat exchanger shown in FIG. 14 of the present invention.

FIG. 17 is a flow chart showing an assembly process of the fin tube type heat exchanger shown in FIG. 14 of the present invention.

FIG. 18 is a plan sectional view showing still another fin-tube heat exchanger according to the first embodiment of the present invention.

FIG. 19 is an explanatory diagram showing a usage example of the fin tube type heat exchanger according to the second embodiment of the present invention.

FIG. 20 is an explanatory diagram showing a flow of condensed water in the fin-tube heat exchanger shown in FIG. 19 according to the second embodiment of the present invention.

FIG. 21 is an explanatory diagram showing a usage example of the fin-tube heat exchanger according to the third embodiment of the present invention.

FIG. 22 is a diagram showing a refrigeration cycle configuration of a refrigeration air-conditioning apparatus according to Embodiment 4 of the present invention.

FIG. 23 is a partial external view showing a plate fin type heat exchanger having a conventional flat heat transfer tube.

FIG. 24 is a partial external view showing another plate fin type heat exchanger having a conventional flat heat transfer tube.

FIG. 25 is an explanatory view showing an assembly method of the conventional plate fin type heat exchanger shown in FIG. 23.

FIG. 26 is an explanatory view illustrating a problem of a conventional method for assembling the plate fin type heat exchanger shown in FIG. 23.

FIG. 27 is a sectional view showing a plate fin type heat exchanger having a conventional tubular heat transfer tube.

[Explanation of symbols]

1 plate fin, 2 heat transfer tube, 3 cut and raised slit,
6 Fin collar, 6c No fin collar, 6
d recess, 8 brazing material, 11 insertion hole, 21 compressor, 2
2 condenser, 23 throttling device, 24 evaporator.

─────────────────────────────────────────────────── ───

[Procedure amendment]

[Submission date] February 13, 2003 (2003.2.1
3)

[Procedure Amendment 1]

[Document name to be amended] Statement

[Name of item to be corrected] Claim 4

[Correction method] Change

[Correction content]

[Procedure Amendment 2]

[Document name to be amended] Statement

[Correction target item name] 0013

[Correction method] Change

[Correction content]

A fin-tube heat exchanger according to a fourth aspect of the present invention is the fin-tube heat exchanger according to any one of the first to third aspects, in which the heat exchange fluid flows in a direction perpendicular to the flow direction. An array of through heat transfer tubes, which are divided so as to divide the major axis diameter of the flat cross section of the flat heat transfer tubes. When the number of through heat transfer tubes is n, the number of plate fins is divided. n + 1.

[Procedure 3]

[Document name to be amended] Statement

[Name of item to be corrected] 0070

[Correction method] Change

[Correction content]

The fin-tube heat exchanger according to claim 4 is the fin-tube heat exchanger according to any one of claims 1 to 3, wherein the fin-tube heat exchanger is arranged in a direction perpendicular to the flow direction of the heat exchange fluid. A through-hole heat transfer tube, which is divided so as to divide the major axis diameter of the flat cross-section of a flat heat transfer tube. When the number of through heat transfer tubes is n, the number of plate fins is n + 1. Therefore, even if the number of through-hole heat transfer tubes arranged is plural, the fin-tube heat exchanger has good assemblability and looks good when completed.

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Kunihiko Kaga             2-3 2-3 Marunouchi, Chiyoda-ku, Tokyo             Inside Ryo Electric Co., Ltd. (72) Inventor Shinji Nakajima             2-3 2-3 Marunouchi, Chiyoda-ku, Tokyo             Inside Ryo Electric Co., Ltd. (72) Inventor Nao Saito             2-3 2-3 Marunouchi, Chiyoda-ku, Tokyo             Inside Ryo Electric Co., Ltd.

Claims (12)

[Claims] 1. A plurality of plate-shaped fins laminated at a predetermined interval, and a cross-section that penetrates the plate-shaped fins in the stacking direction and through which the heat-exchanged fluid flows and the heat-exchanged fluid flows. Includes a plurality of heat transfer tubes having a flat shape, and a plurality of cut and raised slits provided on the plate-shaped fins, by flowing a heat exchange fluid between the plate-shaped fins and between the heat transfer tubes, In the fin tube type heat exchanger for exchanging heat between the heat exchanged fluid and the heat exchange fluid, the heat transfer tube is arranged such that the major axis diameter of the flat cross section is aligned with the flow direction of the heat exchange fluid, There is at least one array of penetrating heat transfer tubes penetrating the plate-shaped fins in a direction perpendicular to the flow direction of the heat exchange fluid, and the cut-and-raised slits provided in the plate-shaped fins are arranged in the vertical direction. Between heat transfer tubes of heat tubes When the widths of the cut-and-raised slits are a and the distances between the cut-and-raised slits are b, the relationship being 1 ≦ b / a ≦ 4. A characteristic fin-tube heat exchanger. 2. The fin-tube heat exchanger according to claim 1, wherein the cut-and-raised slits have the same width. 3. The number of one cut-and-raised slits arranged in parallel to the flow direction of the heat exchange fluid is 2 or more and 6 or less, according to claim 1 or 2. The fin tube type heat exchanger described. 4. The plate-shaped fins divide a major axis diameter of a flat cross section of the flat heat transfer tube in an arrangement direction of the through heat transfer tubes arranged in a direction perpendicular to a flow direction of the heat exchange fluid. The fin according to any one of claims 1 to 3, wherein the plate-shaped fin is divided into n + 1 when the number of through-hole heat transfer tubes arranged is n. Tube type heat exchanger. 5. The plate-shaped fins are arranged at a downstream side end portion in the flow direction of the heat exchange fluid having a major axis diameter of the flat cross section of the flat heat transfer tube, and are arranged in a direction perpendicular to the flow direction of the heat exchange fluid. The fin-tube heat exchanger according to any one of claims 1 to 3, wherein the through-hole heat transfer tubes are arranged and divided in the arrangement direction. 6. The plate-shaped fins are arranged at an upstream side end portion in a flow direction of the heat exchange fluid having a major axis diameter of a flat cross section of the flat heat transfer tube, in a direction perpendicular to the flow direction of the heat exchange fluid. The fin-tube heat exchanger according to any one of claims 1 to 3, wherein the through-hole heat transfer tubes are arranged and divided in the arrangement direction. 7. A fin collar protruding from a plate fin, an insertion hole formed in the plate fin so as to be surrounded by the fin collar and parallel to a flow direction of the heat exchange fluid, A plurality of heat transfer tubes inserted into the fin collar and the insertion hole so that the heat transfer tubes can be arranged in a direction parallel to the flow direction of the exchange fluid, and the heat transfer tubes on the upstream side with respect to the flow direction of the heat exchange fluid. A portion without a fin collar is provided between the heat transfer pipe on the downstream side, and the downstream end portion of the insertion hole and the downstream end portion of the fin collar have a curvature so as to spread outward at the downstream end portion of the plate fin. The fin-tube heat exchanger according to any one of claims 1 to 3, wherein the fin-tube heat exchanger has an opening. 8. When the arrangement of the through heat transfer tubes in the direction perpendicular to the flow direction of the heat exchange fluid is not parallel to the gravity direction and is inclined, the lower end of the through heat transfer tubes is relative to the end. The fin-tube type heat exchanger according to any one of claims 1 to 7, which is located above a lower end of the plate-shaped fin located in the direction of gravity. 9. The heat transfer tube is inserted into an insertion hole formed in a plate-shaped fin and a fin collar protruding from the plate-shaped fin around the insertion hole, and brought into contact with the fin collar through a brazing material layer. The fin-tube heat exchanger according to any one of claims 1 to 8, which is characterized in that. 10. A cross section of a plurality of plate-shaped fins laminated at a predetermined interval, and a plurality of plate-shaped fins penetrating through the plate-shaped fins in the stacking direction, through which the heat-exchanged fluid flows and the heat-exchanged fluid flows. Is a flat shape, and a plurality of heat transfer tubes arranged so that the major axis diameter of the flat cross section matches the flow direction of the heat exchange fluid, heat between the plate fins and between the heat transfer tubes. A method of manufacturing a fin-tube heat exchanger in which heat exchange fluid and heat exchange fluid are heat-exchanged by flowing exchange fluid, the step of forming an insertion hole in the plate-shaped fin, Forming a through hole with a fin collar that has a recessed portion, is provided with a brazing material, and is inclined and protrudes so as to narrow the opening toward the tip, and the plate-shaped fin is provided with the fin collar on one side. , The insertion hole And a step of inserting the heat transfer tube into the insertion hole of the laminated plate-shaped fin, the step of inserting from the insertion hole side to the protruding fin collar side, by heating, And a step of joining the heat transfer tube and the plate-shaped fin via a fin collar, the manufacturing method of the fin-tube heat exchanger. 11. A cross-section in which a plurality of plate-shaped fins laminated at a predetermined interval and the plate-shaped fins penetrate through the plate-shaped fins in the stacking direction so that the heat-exchanged fluid flows inside and the heat-exchanged fluid flows. Is a flat shape, and a plurality of heat transfer tubes arranged so that the major axis diameter of the flat cross section matches the flow direction of the heat exchange fluid, heat between the plate fins and between the heat transfer tubes. In a method of manufacturing a fin tube type heat exchanger in which a heat exchange fluid and a heat exchange fluid are heat-exchanged by flowing an exchange fluid, a step of forming an insertion hole in the plate fin, the fin collar Is projected, and with respect to the flow of the heat exchange fluid,
A step of forming an insertion hole having an opening opening at a downstream end of the plate fin; a step of stacking the plate fin with the fin collar on one side and aligning the insertion holes; A step of inserting an upstream heat transfer tube into the insertion hole of the laminated plate fin, a step of inserting an upstream heat transfer tube into the insertion hole from the opening, and a rod-shaped brazing material into the insertion hole. A step of inserting, a step of inserting a heat transfer tube on the downstream side into the insertion hole of the laminated plate fin, a step of inserting a heat transfer tube on the downstream side from the opening into the insertion hole, and heating. And a step of joining the heat transfer tube and the plate-shaped fin via a fin collar. 12. A refrigeration cycle having a compressor, a condenser, a throttle device, and an evaporator, wherein the refrigerant is a heat exchange fluid.
In addition, a refrigerating air conditioner using air as a heat exchange fluid,
At least one of the condenser and the evaporator,
A fin-tube heat exchanger according to any one of claims 1 to 9 is used, or a fin-tube heat exchanger manufactured by the manufacturing method according to claim 10 or 11 is used. Refrigerating and air-conditioning system.