JP2001012883A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To perform a reduction in width without lowering performance of a heat exchanger by forming a width of the exchanger in a ventilating direction of the air flowing through corrugated fins in a specific range, and setting an inclining angle of louvers to the ventilating direction to a specific range. SOLUTION: In the heat exchanger, a width of a wind direction is desired to be formed in a range of 30 to 57 mm to deal with a space conservation of an air conditioner itself and a space conservation of a vehicle itself. Each of fins 5 has bends 11a, 11b brought into contact with and connected to a refrigerant channel of a tube element 4 and flat parts 12 disposed between the bends 11b brought into contact with one tube element 4, and has a predetermined fin height Fh corresponding to a distance between the channels of the adjacent elements 4, and a fin pitch Fp of a distance between the vertexes of the bends 11a brought into contact with and connected to the one side element 4. An angle of the louver is set to 28 to 55 deg..

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigeration cycle mounted on a vehicle, and more particularly to a heat exchanger having fins formed in a corrugated shape, which is used as an evaporator.

[0002]

2. Description of the Related Art A conventional heat exchanger is disclosed in JP-A-7-16.
No. 7578 discloses a laminated heat exchanger in which the width of the fin in the ventilation direction is 50 mm or more and 65 mm or less. In the laminated heat exchanger having a width in the ventilation direction of 50 mm or more and 65 mm or less, the optimum fin where heat exchange efficiency and airflow resistance are folded has a fin height FH of 7.0 mm or more and 9.0 mm.
And the fin pitch FP is 2.0 mm or more and 3.6.
mm or less and the fin thickness is 0.06 mm or more.
The reference discloses that the fin is 10 mm or less.

[0003]

However, in the above-described laminated heat exchanger, the surface of the heat exchanger is coated with a corrosion-resistant film, and a hydrophilic film is further coated thereon, but the heat exchange efficiency is improved. If the fin pitch is made narrower, the drainage of the condensed water adhering to the fins will be reduced, and conversely, the heat exchange efficiency will be reduced and the condensed water will freeze. Occurs.

[0004] In recent years, while demands for downsizing and thinning of heat exchangers have become stronger, they have been used in refrigeration cycles using carbon dioxide as a refrigerant, and as in cooling and heating cycles, evaporators have been used as condensers. When used, a structure that can withstand high pressure has been desired.

[0005] As described above, an object of the present invention is to provide a heat exchanger having a reduced width without deteriorating the performance of the heat exchanger.

[0006]

SUMMARY OF THE INVENTION Accordingly, the present invention has at least a tube element through which a coolant flows, and a corrugated fin disposed between the tube elements, wherein the corrugated fin is in contact with the vent element. And a flat portion located between a vent portion abutting on one tube element and a vent portion abutting on the other tube element, and the flat portion extends in a direction perpendicular to the ventilation direction. In the heat exchanger in which a plurality of louvers are sequentially formed in the ventilation direction, the width of the heat exchanger in the ventilation direction of the air flowing through the corrugated fin is formed within a range of 30 mm or more and 57 mm or less, and the louvers with respect to the ventilation direction are formed. The inclination angle is set to 28 ° or more and 55 ° or less.

[0007] The width in the ventilation direction is 30 mm or more and 57 m
m or less, in order to improve the heat exchange efficiency, when the angle of the louver formed on the fin is changed, the cooling performance is structured by increasing the louver angle,
There is also a problem that the ventilation resistance increases. For this reason,
As a result of an experiment in which the relationship between the louver angle and a factor represented by the cooling performance / airflow resistance (proportional to the cooling capacity and inversely proportional to the airflow resistance) was performed by changing the louver angle, the inclination angle of the louver with respect to the ventilation direction was obtained. Is about 42 °, the maximum value of the above factor can be obtained, and a range of 28 ° to 55 ° can be set as a range satisfying a desired condition (about 80% of the maximum value). .

In an experiment for determining the relationship between the fin pitch and the above-described factor, the fin pitch between a bent portion in contact with one tube element and the next bent portion in contact with one tube element is substantially equal. At 3.8 mm, the maximum value of the factor can be obtained and approximately 3.0
The desired condition can be satisfied in the range of not less than 5.0 mm and not more than 5.0 mm, and the fin height can obtain the maximum value of the above factor at about 7.5 mm and about 5.0.
The desired condition can be satisfied within the range of not less than mm and not more than 9.5 mm. In addition, it is desirable that the interval between the tube elements is formed in accordance with the fin height by setting the fin height.

Further, in forming the louver, it is preferable that a distance between an end of the louver and the tube element be within a range of approximately 0.2 mm or more and 1.5 mm or less. Fin thickness
It is desirable that the thickness be 0.09 mm or more and 0.2 mm or less.

In the above conditions, the heat exchanger is disposed between a tube element having a pair of tank portions formed at at least one end in the longitudinal direction and a refrigerant passage communicating with the tank portions, and the tube element. The present invention is applicable to a stacked heat exchanger formed by alternately stacking corrugated fins.

Further, in the laminated heat exchanger, the tube element may include a pair of upper tanks formed at one end in the longitudinal direction, a pair of lower tanks formed at the other end in the longitudinal direction, and the upper tank. A two-tank heat exchanger having a first refrigerant passage communicating one of the lower tanks with one of the lower tanks, and a second refrigerant passage communicating the other of the upper tank with the other of the lower tanks. Further, the tube element may further include a pair of tank portions formed at one end in the longitudinal direction, and a U communicating with the pair of tank portions.
It may be a single tank type heat exchanger having a U-shaped passage.

[0012]

Embodiments of the present invention will be described below with reference to the drawings.

The heat exchanger 1 shown in FIGS. 1 (a) and 1 (b)
A one-tank stacked heat exchanger, comprising a pair of tank portions 2 and 2 formed at one end in the longitudinal direction;
, A plurality of tube elements 4 each including a refrigerant passage 3 communicating with each other, and a refrigerant passage 3 of the tube element 4.
And a corrugated fin 5 disposed therebetween. In the heat exchanger 1 shown in FIGS. 1A and 1B, end plates 6 and 6 are arranged at both ends of the tube element 4 and the fins 5 in the stacking direction, and the tube element located substantially at the center in the stacking direction. 4 'has a blind tank portion 2' that divides one of a pair of tank groups 7, 7 formed by communicating the tank portion 2 in the stacking direction into two tank blocks 7A, 7B.

At an approximate center of the tank block 7A, an inlet-side mounting portion 8 for mounting a refrigerant inflow pipe (not shown) extends from the tank portion 2 along the direction of air flow. Formed and the tank block 7B
An outlet-side mounting portion 9 for mounting a refrigerant outflow pipe (not shown) is formed at substantially the center of the tank so as to extend from the tank portion 2 along the direction of air flow.

Accordingly, the refrigerant flowing into the tank block 7A from the inflow pipe mounted on the inlet side mounting portion 8 flows through the refrigerant flow path 3 to the tank group 7 on the other side,
It moves within this tank group 7. The refrigerant that has moved through the other tank group 7 passes through the refrigerant flow path 3 and moves to the tank block 7B, and flows out to the refrigerant outflow pipe mounted on the outlet-side mounting portion 9. is there.

In the heat exchanger 1 having the above configuration, the width Cw in the ventilation direction is formed in the range of 30 mm or more and 57 mm or less in order to save the space of the air conditioner itself or the space of the vehicle itself. Is required. And in this Embodiment, width Cw of heat exchanger 1 is formed as 40 mm.

As shown in FIGS. 2 to 4, the fins 5 are provided with vent portions 11a and 11b which are in contact with the refrigerant flow path 3 of the tube element 4 and a vent portion which is in contact with one of the tube elements 4. A predetermined fin height Fh corresponding to a space between the refrigerant flow passages 3 of adjacent tube elements 4, having a flat portion 12 located between 11 a and a vent portion 11 b in contact with the other tube element 4; And a fin pitch Fp between the vertices of the vent portion 11a that is in contact with the one tube element 4.

The fins 5 are formed with a plurality of louvers 10 extending vertically in the ventilation direction in such a manner as to be cut and raised in order in the ventilation direction, so that the air passing along the fins 5 passes along the louvers 10. The fins 5 can cross the fins 5 so that the heat exchange capacity can be increased by increasing the inclination angle (louver angle) Ra of the louvers with respect to the flat portion 12 of the fins 5. When the louver angle Ra is increased, the ventilation resistance is increased and the heat exchange capacity is reduced.

From the above, the width in the ventilation direction is 40 mm.
In the heat exchanger, an experiment was performed by changing the louver angle Ra to find a factor indicating the cooling performance and a factor indicating the ventilation resistance, and from these factors, a factor indicating the overall capacity of the heat exchanger (heat exchanger capacity). Fa was determined (Fa = cooling performance / ventilation resistance). The heat exchanger capacity Fa is proportional to the cooling capacity and inversely proportional to the ventilation resistance.

This louver angle R obtained by experiment
FIG. 5 is a characteristic diagram showing the relationship between the heat exchanger capacity Fa and the heat exchanger capacity Fa.
It can be seen that the maximum capacity is obtained when the louver angle Ra is approximately 42 °. And this maximum ability is 1
A range that is 80% or more when the ratio is set to 00% is defined as an appropriate range Ras of the louver angle Ra. The proper range Ras is 28 ° or more and 5 ° from the characteristic diagram shown in FIG.
The range is 5 ° or less.

Similarly, the relationship between the fin pitch Fp and the heat exchanger capacity Fa obtained by an experiment is shown in FIG. 6, and the fin pitch Fp is about 4.
It can be seen that the maximum capacity is obtained at 0 mm. Then, as in the case described above, the heat exchanger capacity Fa is 80% of the maximum.
Assuming that the above range is an appropriate range Fps of the fin pitch Fp, the appropriate range Fps is 3.0 mm or more and 5.0 mm or less according to the characteristic diagram shown in FIG.

FIG. 7 shows the relationship between the fin height Fh and the heat exchanger capacity Fa obtained by experiments.
It can be seen that the maximum capacity is obtained when the fin height Fh is about 7.5 mm. Assuming that the range in which the heat exchanger capacity Fa is 80% or more of the maximum is the appropriate range Fhs of the fin height Fh, as in the case described above, the appropriate range Fhs is obtained from the characteristic diagram shown in FIG. , 5.
It becomes 0 mm or more and 9.5 mm or less. In addition, it is necessary to form a width between the refrigerant flow paths 3 of the adjacent tube elements 4 in accordance with the fin height Fh.

The fin plate thickness Ft is preferably as thin as possible in terms of cost. However, in order to increase the fin strength, the fin plate thickness needs to be more than a predetermined value. It is desirable to set it within the range of not less than 0.2 mm and not more than 0.2 mm. Further, the distance Dr between the end of the louver 10 formed on the fin 5 and the vertices of the vents 11a and 11b of the fin is desirably 0.2 mm or more and 1.5 mm or less. By setting the distance Dr within this range, the drainage of the fins can be improved, and the fin strength when the fins are formed in a corrugated shape can be maintained. Further, the joining property between the fin 5 and the tube element 4 by brazing can be improved.

In the above heat exchanger 1, the width Cw in the ventilation direction is set to 40 mm as described above. However, as shown in FIG. 8, the heat width in the ventilation direction is set in the range of 30 mm to 57 mm. In the exchanger, the various appropriate ranges described above could be obtained.

A heat exchanger 30 shown in FIG. 9 shows another embodiment of the above-described heat exchanger 1, and the shape of the fins 5 and the shape of the louver 10 are the same as those of the heat exchanger 1. What can be used.

The heat exchanger 30 has a pair of upper tank portions 31 and 32 formed at one longitudinal end, a pair of lower tank portions 33 and 34 formed at the other longitudinal end, and one upper tank portion. A plurality of tubes each having a first refrigerant flow path 35 that communicates with the first lower tank part 33 and a second refrigerant flow path 36 that communicates with the other upper tank part 32 and the other lower tank part. It has an element 37, and the fin 5 of the condition described above is arranged between the tube element 37. Thereby, the width of the heat exchanger 30 along the ventilation direction can be formed to be 30 mm or more and 57 mm or less. Reference numeral 44 denotes end plates disposed at both ends in the stacking direction.

The heat exchanger 30 is connected to the tank 3
1, 32, 33, and 34 have four tank groups 38, 39, 40, and 41 configured to communicate in the stacking direction. A refrigerant inlet pipe 42 communicates with a first tank group 38 including one upper tank portion 31, and the other upper tank portion 32
A fourth tank group 41 composed of
Is communicated. In addition, a second tank group 39 including one lower tank section 33 and a third tank group 40 including the other lower tank section 34 include an opening 45 formed at an end of the second tank group 39, The bypass passage 44 and the third tank group 40 communicate with each other through an opening 46 formed at an end of the tank group 40.

With the above arrangement, the refrigerant flowing from the refrigerant inlet pipe 42 flows from the first tank group 38 through the first refrigerant flow path 35 to the second tank group 39, and the bypass flow path 44 Through the second tank flow path 35, flows into the fourth tank group 41, and flows out of the refrigerant outlet pipe 43.

[0029]

As described above, according to the present invention, in a heat exchanger having a width in the ventilation direction of 35 mm or more and 57 mm or less, the angle of the louver is set to 28 ° to 55 °.
° or less, the fin pitch is 3.0 mm
Since the capacity of the heat exchanger can be secured to a predetermined value or more even when the thickness is 5.0 mm or less, the drainage of the fins can be improved while maintaining the performance of the heat exchanger.

[Brief description of the drawings]

FIG. 1A is a front view showing a one-tank stacked heat exchanger according to an embodiment of the present invention;
(B) is a side view thereof.

FIG. 2A is a front view showing a fin height Fh of the fin, and FIG. 2B is a cross-sectional view thereof.

FIG. 3 is a partially enlarged sectional view showing a louver angle Ra of a fin.

FIG. 4 is a schematic side view showing a fin pitch Fp, a fin height Fp, and a distance Dr between a louver end and a top of a vent.

FIG. 5 is a characteristic diagram showing a relationship between a louver angle Ra and a heat exchanger capacity Fa.

FIG. 6 is a characteristic diagram showing a relationship between a fin pitch Fp and a heat exchanger capacity Fa.

FIG. 7 is a characteristic diagram showing a relationship between a fin height Fh and a heat exchanger capacity Fa.

FIG. 8 shows the width Cw of the heat exchanger in the ventilation direction and the capacity F of the heat exchanger.
FIG. 3 is a characteristic diagram showing a relationship with a.

FIG. 9 is a perspective view showing a double-tank stacked heat exchanger in the heat exchanger according to the embodiment of the present invention.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Heat exchanger 4 Tube element 5 Fin 10 Louver 11a, 11b Vent part 12 Flat part

Claims (8)

[Claims] 1. A tube element through which at least a coolant flows, and a corrugated fin disposed between the tube elements, wherein the corrugated fin is in contact with the tube element and a vent is in contact with one of the tube elements. A plurality of louvers extending in a direction perpendicular to the ventilation direction, and a plurality of louvers extending in the direction perpendicular to the ventilation direction are sequentially formed in the flat portion. The width of the heat exchanger in the ventilation direction of the air flowing through the corrugated fin is formed within a range of 30 mm or more and 57 mm or less, and the inclination angle of the louver with respect to the ventilation direction is 28 ° or more and 55 ° or more.
° or less. 2. In each of said corrugated fins,
2. A fin pitch between a bent portion in contact with one tube element and a next bent portion in contact with one tube element is approximately 3.0 mm or more and 5.0 mm or less. The heat exchanger as described. 3. In each of the corrugated fins,
The fin height is formed in a range of about 5.0 mm or more and 9.5 mm or less, and the interval between the tube elements is formed corresponding to the fin height. Heat exchanger. 4. The heat exchange according to claim 1, wherein a distance between an end of the louver and the tube element is in a range of about 0.2 mm or more and 1.5 mm or less. vessel. 5. The plate thickness of said corrugated fin is 0.0
The heat exchanger according to any one of claims 1 to 4, wherein the heat exchanger has a length of 9 mm or more and 0.2 mm or less. 6. The heat exchanger includes a tube element having a pair of tank portions formed at at least one end in a longitudinal direction and a refrigerant passage communicating with the tank portions, and a corrugated fin arranged between the tube elements. The heat exchanger according to any one of claims 1 to 5, wherein the heat exchanger is a stacked heat exchanger formed by alternately stacking. 7. A pair of upper tanks formed at one end in the longitudinal direction, a pair of lower tanks formed at the other end in the longitudinal direction, and one of the upper tank and one of the lower tanks. 7. A double-tank heat exchanger having a first refrigerant passage communicating with a second refrigerant passage and a second refrigerant passage communicating the other of the upper tank portion with the other of the lower tank portion. The heat exchanger as described. 8. The heat exchanger according to claim 1, wherein the tube element is a single-tank heat exchanger having a pair of tank portions formed at one longitudinal end and a U-shaped passage communicating the pair of tank portions. Item 7. A heat exchanger according to Item 6.