JP2002372340A - Condenser - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a thin condenser having the greater amount of heat radiation per operating power. SOLUTION: In a thin condenser with the thickness of a core being 16 mm or less, a characteristic value of a basic configuration is assumed 0.65 or less. Hereby, a large condenser having large rate of heat radiation/(air power + refrigerant power) is obtained. Herein, the characteristic value of a basic configuration = (height of fin + height of tube)/core thickness<1/2> }× 1/(surface area in tube<1/5> /tube flatness<3/4> )}.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a condenser for use in, for example, a refrigeration cycle of a vehicle air conditioning system.

[0002]

2. Description of the Related Art A condenser of this type comprises a pair of tanks disposed opposite each other at a predetermined interval, a plurality of tubes communicating with the two tanks, and a fin joined between the tubes. It has a core part made of. Each of the tanks is provided with a partition plate, and the partition of the partition plate allows the refrigerant to meander between the two tanks through a plurality of tubes. An inner fin is provided inside the tube to form a pressure-resistant structure and to increase the contact area with the refrigerant.

In recent years, the thickness of such a condenser has been reduced due to demands for reduction in weight and space in a vehicle, and the thickness of a core portion is about to reach 16 mm or less.

[0004]

However, since such a reduction in thickness is based on the restriction of the space for mounting the vehicle in the first place, the front area of the core is also restricted, and the thickness is simply reduced. In this case, the contact area with the air and the contact area with the refrigerant are reduced, and the heat radiation amount is reduced. Furthermore, the resistance of the refrigerant passage increases due to the decrease in the cross-sectional area of the refrigerant passage, the flow rate of the refrigerant decreases, and the amount of heat radiation further decreases.

On the other hand, if an attempt is made to increase the amount of heat radiation while reducing the thickness, a blowing means (fan) or a cooling medium means (compressor) is required.
A large amount of air power (power needed to send air) and refrigerant power (power needed to send refrigerant), that is, energy-inefficient condensation It becomes a vessel. In particular, in a condenser where the circulation of the refrigerant greatly affects the heat radiation performance, the amount of heat radiation per refrigerant power cannot be ignored.

The present invention has been made on the background of the prior art, and derives a preferable relationship among core thickness, fin height, and tube height which determine the basic shape of the condenser, It is an object of the present invention to provide a condenser that is thin and has a large amount of heat radiation per operation power.

[0007]

[MEANS FOR SOLVING THE PROBLEMS] Under such a purpose,
When selecting a condenser with a high heat dissipation / (air power + refrigerant power), instead of individually specifying each factor relating to the basic shape of the condenser as in the past, these factors are comprehensively determined. Based on the prediction that it is most effective to consider and set each factor, as a result of repeated research, we have comprehensively specified the interrelationship of these factors, and Find the basic shape characteristic value that can organize the power together, and based on this basic shape characteristic value,
Thus, a condenser that is thin and has a large amount of heat radiation per operation power has been provided.

[0008]

(Equation 2)

Based on the evaluation values of the heat release amount / air power and the heat release amount / refrigerant power based on the basic shape characteristic value, the basic shape characteristic value ≦ 0 even in a thin condenser having a core thickness of 16 mm or less. It was found that when the ratio was 0.65, a condenser having a large heat release amount / (air power + refrigerant power) could be provided.

Therefore, according to the first aspect of the present invention,
Between a pair of tanks arranged facing each other at a predetermined interval,
A plurality of flat tubes communicating with the pair of tanks,
A condenser comprising a corrugated fin joined between the plurality of tubes and an inner fin in each tube, wherein a core thickness ≦ 16 m
m, and the basic shape characteristic value ≦ 0.65.

[0011]

According to the first aspect of the present invention, the core thickness ≦
Since 16 mm and the basic shape characteristic value ≦ 0.65, it is possible to provide a thin condenser having a large heat radiation amount per operation power.

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of a condenser according to the present invention will be described below with reference to the drawings. 1 and 2 are views showing a condenser according to this embodiment. The condenser 1 is made of an aluminum alloy and has a plurality of flat plates communicating between the pair of tanks 2 and 2 between the pair of tanks 2 and 2 which are opposed to each other at a predetermined interval as shown in FIG. And a fin 4 joined between the plurality of tubes 3.

The flat tube 3 is provided with inner fins 5 called so-called offset fins therein, so as to constitute a pressure-resistant structure and to increase the contact area with the refrigerant.

The fins 4 are bent in a corrugated shape and have substantially the same width as the tube 2. The fin 4 has a louver 6 cut into its wall surface.

The surface of one of the tube 3 and the fin 4 is formed of a brazing material.
The plurality of tubes 3 and the fins 4 are brazed to each other in an alternately stacked state.

The tank 2 is provided with tube insertion ports 7 at intervals along the longitudinal direction of the tank 2, and the open end of the tube 3 is inserted into the tube insertion port 7 and brazed. Interconnected. Further, each tank 2 is provided with one partition plate 8, and a plurality of tubes 3 communicating with each tank 2 are divided into three passage groups A, B, and C by the division of the partition plate 8. Has been split. A refrigerant inlet 9 for introducing refrigerant discharged from a compressor of a refrigeration cycle (not shown) is provided at an upper end of one of the tanks 2 (the left tank in FIG. 1). (1 tank on the right)
A refrigerant outlet 10 for discharging the refrigerant is provided.

With such a structure, as shown in FIG. 1B, the refrigerant flowing from the refrigerant inlet 9 flows between the two tanks 2 in the order of the first passage group A → the second passage group B → the third passage group C. , And flows out of the medium outlet 10. In FIG. 1A, reference numeral 11 denotes a side plate joined to the outermost fin 4.

The condenser 1 of the present embodiment having such a basic structure has a core thickness of 16 mm or less in order to reduce the thickness. When the “basic shape specific value” is 0.
The basic shape is selected so as to be 65 or less.

[0019]

(Equation 3)

The above-mentioned "basic shape characteristic value" has been conceived by the present inventor as a parameter that can organize both the heat radiation amount / air power and the heat radiation amount / refrigerant power. .

The amount of heat released from the condenser 1 and the power of the air and the power of the refrigerant are determined from the contact area with the air, the ventilation resistance, the contact area with the refrigerant, and the pipe resistance. The most basic form factor is the fin width (= Core thickness), fin height, tube width (= core thickness), tube height, and tube cross-sectional shape.

Here, under the same core size, the same refrigerant condition (refrigerant temperature, refrigerant pressure, refrigerant flow rate) and the same air condition (air temperature, air pressure, air flow rate), the thickness of the fin 4 is constant, and the fin pitch is set. Focusing on the fact that the heat radiation amount / air power of one fin 4 can be arranged by a parameter of fin height / (core thickness) ^1/2 as shown in FIG. Heat dissipation /
Pneumatic power (fin height + tube height) / (core thickness)
^It was predicted that the shape parameter could be reduced to ２.

On the other hand, focusing on the fact that the contact area with the refrigerant and the pipe resistance can both be determined from the hydraulic diameter of the tube 3 (= tube cross-sectional area / tube internal surface area), the present inventor has determined that the heat radiation amount / It was predicted that the refrigerant power could be organized by a shape parameter of 1 / {tube inner surface area ^1/5 / tube flatness ^3/4 }.

Then, the above-mentioned shape parameter of (fin height + tube height) / core thickness ^1/2 , and 1 /
｛Tube inner surface area ^1/5 / Tube flatness ^3/4 ｝
The product of the above-mentioned shape parameters and the basic shape characteristic value of the condenser 1 was used as the basic shape characteristic value, and the experimental values of the heat release amount / air power and the heat release amount / refrigerant power were evaluated based on the basic shape characteristic value. The graphs shown in FIGS. 4 to 8 below are calculation results calculated based on experimental values.

By the way, actually, while keeping the air receiving area of the core portion constant, other shape factors other than the basic shape (the thickness of the fins 4, the fin pitch of the fins 4, the thickness of the tubes 3, the thickness of the inner fins 5, With the plate thickness, the fin pitch of the inner fins 5, the louver pitch, and the louver angle being kept constant, the heat release / pneumatic power was evaluated based on the basic shape characteristic values described above. 4 to 6 show the wind receiving area of the core portion = 30.
0 × 700 mm ² , fin 4 thickness = 0.1 mm, fin 4 fin pitch = 1.5 mm, tube 3 thickness =
0.32 mm, thickness of inner fin 5 = 0.32 m
m, fin pitch of the inner fin 5 = 3 mm, louver pitch = 1 mm, louver angle = 20 ° and experimental data and simulation data corresponding thereto. Then, as predicted by the inventor, it was found that there was a specific relationship between the basic shape characteristic value and the heat release / air power (see FIG. 4). Here, the heat release amount / pneumatic power has the maximum value when the basic shape characteristic value = 0.65.

On the other hand, when the heat release amount / coolant power is evaluated based on the basic shape characteristic value, as shown in FIG. 5, the heat release amount / coolant power decreases to the right with respect to the basic shape characteristic value. In other words, it is desirable that the smaller the basic shape characteristic value is, the more the heat release amount / coolant power is considered.

Now, in order to select a condenser 1 having high energy efficiency, the ratio of the air power to the refrigerant power with respect to the total operating power of the condenser 1 is examined. As shown in FIG. Is less than about 30 percent, indicating that most of the total power is dependent on refrigerant power. In particular, when the basic shape characteristic value is large, the refrigerant power accounts for about 90% or more of the total power. Therefore, in order to increase the heat radiation amount / total power, the basic shape characteristic value ≦ 0.65 should be considered in consideration of the fact that the heat radiation amount / air power shows a peak at the basic shape characteristic value = 0.65. The condenser 1 according to the present embodiment, in which the core thickness is ≤16 and the basic shape characteristic value is ≤0.65, is a thin condenser with high heat dissipation / total power and high energy efficiency.

Here, shape factors other than the above-described basic shape characteristic values (the air receiving area of the core portion, the plate thickness of the fin 4, the fin pitch of the fin 4, the plate thickness of the tube 3, the louver pitch, and the louver angle) are variables. When the performance was evaluated for the case of と し た, the following results were obtained. First, regardless of whether the air receiving area of the core is widened or narrowed, the heat release amount / air power shows a peak at the basic shape value = 0.65, and the heat release amount / coolant power is higher than the basic shape characteristic value. The refrigerant power in the total power accounted for 70% or more. Therefore, if the basic shape characteristic value ≦ 0.65 irrespective of the air receiving area of the core portion, the condenser has high energy efficiency.

Considering the shape factors of the ventilation resistance other than the basic shape (the fin pitch of the fins 4 and the plate thickness of the fins 4), first, when the fin pitch is a variable, as shown in FIG. However, since the heat radiation amount / coolant power always shows a peak at the basic shape characteristic value = 0.65, the core thickness ≦ 1 as described above in this case as well.
It can be seen that by setting the basic shape characteristic value ≦ 0.65 and a heat radiation amount / total power, a thin condenser with high energy efficiency can be provided. Also, fin 4
When the thickness of the sheet is a variable, the basic shape characteristic value =
The heat radiation amount / coolant power always peaks at 0.65, and the same can be said. The same was true even when the louver pitch and the louver angle of the louvers formed on the fins 4 were changed.

In the above evaluation, the evaluation is performed with the fin pitch of the inner fin 5 and the plate thickness of the inner fin 5 being constants of one variable of the basic shape characteristic value.
Actually, when the factors of the pipeline resistance (the fin pitch of the inner fin 5 and the thickness of the inner fin 5) as variables are considered as variables, first,
When the fin pitch of the inner fin 5 is set to various values, the heat radiation amount / air power always shows a peak at the basic shape characteristic value = 0.65, and the heat radiation amount / coolant power is rightward relative to the basic shape characteristic value. I fell down. The same applies to the case where the thickness of the inner fin 5 is used as a variable. In other words, if the basic shape characteristic value with the core thickness specifying the basic shape, the tube height, the fin height, and the tube cross-sectional shape being 0.65 or less, the heat dissipation / total power is large and the energy efficiency is high. The condenser 1 can be provided. Here, the larger the fin pitch of the inner fins 5, the smaller the amount of heat release / refrigerant power and refrigerant power / total power, but even if the fin pitch of the inner fins 5 is the largest,
Even when only one inner fin 5 stands in the tube 3, the refrigerant power / total power is 5
0% or less, it is possible to use a region of high heat radiation amount / coolant power, and as described above, the core thickness ≦
When 16 and the basic shape characteristic value ≦ 0.65, it is possible to provide a thin condenser having a large heat radiation amount / total power and high energy efficiency. The inner fin of the present invention may be an insertion type inner fin 5 formed separately from the tube 3 and inserted into the tube 3 as in this embodiment, or may be formed by extruding the tube. The inner fin may be an integral type integrally formed with the tube.

In the above evaluation, the core thickness, which is one variable of the basic shape characteristic value, is evaluated as core thickness = tube width = fin width. However, the present invention is also applicable to the case where the fin width is larger than the tube width. Applied. That is, even when the fin width is larger than the tube width, the heat radiation amount / air power always shows a peak at the basic shape characteristic value = 0.65,
By setting the core thickness ≦ 16 and the basic shape characteristic value ≦ 0.65, it is possible to provide a thin condenser having high heat dissipation / total power and high energy efficiency. In the case of tube width <fin width, core thickness = fin width.

In short, if the characteristic value of the basic shape having the core thickness, tube height, fin height and tube cross-sectional shape for specifying the basic shape as variables is 0.65 or less, the amount of heat radiation / total power is large. , Energy efficient condenser 1
Can be provided.

Now, such a basic shape characteristic value ≦ 0.6
In the condenser 1 of No. 5, a more preferable shape is limited as follows.

Considering the heat radiation characteristics of the fin alone, when the fin plate thickness is 0.1 mm and the fin pitch is 1.5 mm, the effect of the fin height on the heat radiation is shown in FIG. It is known that the amount of heat radiation increases in the range of fin height ≦ 8. Therefore, in a structure having a core thickness of ≤16 mm, the above-described basic shape characteristic value ≤0.65 is required for the condenser 1 having a large heat radiation amount / total power and a large heat radiation amount.
May be set within the range of 5.5 ≦ fin height ≦ 8.

In the case where the height of the tube is limited to 1.8 mm or less in order to further reduce the size of the condenser, the range of the basic shape characteristic value ≦ 0.65 is indicated by a circle in FIG.
The condenser indicated by the mark and having the basic shape in this range is the most preferable structure that is small and lightweight, has good energy efficiency, and has a large amount of heat radiation.

As described above, according to this embodiment, since the core thickness ≦ 16 and the basic shape characteristic value ≦ 0.65, a thin condenser with high energy efficiency can be provided.

Further, when 5.5 ≦ fin height ≦ 8, it is possible to provide a thin condenser having a large amount of heat radiation while increasing energy efficiency.

Further, when the tube height is 1.8 mm or less, it is possible to provide the thin condenser 1 which is small and lightweight, has good energy efficiency, and has a large amount of heat radiation. The basic shape characteristic value has a lower limit of 0.
35, 0.35 ≦ the basic shape characteristic value ≦
0.65 is sufficient.

[Brief description of the drawings]

FIG. 1 is a schematic view of a condenser according to an embodiment of the present invention. FIG. 1A is a front view of the condenser, and FIG. 1B is a view showing the flow of refrigerant in the condenser.

FIG. 2 is an exploded perspective view showing a mutually joined state of a tube, a fin, and a tank of the condenser of FIG. 1;

FIG. 3 Heat release amount of fins alone / air power and fin height /
The figure which shows the relationship with the core thickness ² .

FIG. 4 is a diagram showing a relationship between a basic shape characteristic value and a heat radiation amount / pneumatic power according to the present invention.

FIG. 5 is a diagram showing a relationship between a basic shape characteristic value and a heat radiation amount / refrigerant power according to the present invention.

FIG. 6 is a diagram showing a relationship between a basic shape characteristic value and pneumatic power / total power according to the present invention.

FIG. 7 is a diagram showing a relationship between a basic shape characteristic value and a heat radiation amount / pneumatic power when a value of a fin pitch is changed.

FIG. 8 is a diagram showing a relationship between fin height and heat radiation.

FIG. 9 is a diagram showing a range of a basic shape characteristic value ≦ 0.65 in a core thickness ≦ 16, 5.5 ≦ fin height ≦ 8, and a tube height ≦ 1.8.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Condenser 2 Tank 3 Tube 4 Fin 5 Inner fin

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Toshiaki Yamamoto 5-24-15 Minamidai, Nakano-ku, Tokyo Inside Calsonic Nick Kansei Corporation (72) Inventor Shogo Shinhama 5-24-15 Minamidai, Nakano-ku, Tokyo (72) Inventor Mitsuru Iwasaki 5-24-15 Minamidai, Nakano-ku, Tokyo F-term in Calsonic Kansei Corporation (Reference) 3L103 AA05 AA36 BB38 DD15 DD54 DD55

Claims (1)

[Claims] A plurality of flat tubes (3) communicating with a pair of tanks (2, 2) are provided between a pair of tanks (2, 2) arranged facing each other at a predetermined interval; A condenser (1) comprising a core portion composed of a corrugated fin (4) joined between a plurality of tubes (3), and an inner fin (5) provided inside each of the tubes (3). 2. The condenser according to claim 1, wherein the core thickness ≤ 16 mm and the basic shape characteristic value ≤ 0.65. (Equation 1)