WO2001001058A1

WO2001001058A1 - Heat exchanger

Info

Publication number: WO2001001058A1
Application number: PCT/JP2000/001808
Authority: WO
Inventors: Kunihiko Nishishita
Original assignee: Zexel Valeo Climate Control Corporation
Priority date: 1999-06-30
Filing date: 2000-03-24
Publication date: 2001-01-04
Also published as: JP2001012883A

Abstract

A heat exchanger having a width of 30 mm or longer to 57 mm or shorter in ventilating direction capable of eliminating such defects that, when the angle of a louver formed in a fin is varied in order to increase a heat exchange efficiency, though a cooling performance is increased when a louver angle is increased, a ventilating resistance is increased, wherein, based on an experiment to obtain a relationship between the louver angle and a factor (capacity of heat exchanger) indicated by the cooling performance/ventilating resistance carried out by varying the louver angle, the maximum value of the factor can be obtained when an inclination angle relative to a louver ventilating direction is approx. 42°, and an appropriate angle to meet the desired requirements (approx. 80% of the maximum value) is within the range of 28° or higher and 55° or lower.

Description

Description Heat exchanger Technical field

The present invention relates to a heat exchanger having a fin formed in a corrugated shape, which is used for a refrigeration cycle mounted on a vehicle, and particularly used as an evaporator. Background art

As a conventional heat exchanger, Japanese Patent Application Laid-Open No. 7-167578 discloses a laminated heat exchanger in which the width of a fin in the ventilation direction is 50 mm or more and 65 mm or less. In a stacked heat exchanger with a width in the ventilation direction of 50 mm or more and 65 mm or less, the best fin that balances heat exchange efficiency and airflow resistance is a fin height FH of 7.0 mm or more. The reference discloses that the fin is 9.0 mm or less, 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 and 0.10 mm or less. .

However, in the above-described stacked heat exchanger, the surface of the heat exchanger is coated with a corrosion-resistant film, and a hydrophilic film is further coated thereon. Then, the drainage of the condensed water adhering to the fins is reduced, and conversely, the heat exchange efficiency is reduced and the condensed water freezes, so that the fin pitch cannot be reduced.

In recent years, while demands for downsizing and thinning of heat exchangers have become stronger, they have been used in refrigeration cycles that use carbon dioxide as refrigerant, and evaporators have been used as condensers, as in cooling and heating cycles. Withstand high pressure from time to time Such a structure is being desired.

In view of the 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. Disclosure of the invention

Therefore, the present invention has at least a tube element through which a refrigerant flows, and a corrugated fin disposed between the tube elements, wherein the corrugated fin has a vent portion in contact with the tube element, and one of the tube elements And a flat portion located between the vent portion in contact with the other tube element, and the flat portion includes a plurality of loops extending in a direction perpendicular to the ventilation direction. In the heat exchanger formed in order 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 louver tilt angle should be between 28 ° and 55 °.

In a heat exchanger with a width in the ventilation direction of 30 mm or more and 57 mm or less, if the angle of the louver formed on the fin is changed to increase the heat exchange efficiency, the louver angle may be increased. Although the cooling performance is structured, there is a problem that the ventilation resistance increases. For this reason, we conducted experiments to change the louver angle and to determine the relationship between the louver angle and the factor indicated by cooling performance / airflow resistance (proportional to cooling capacity and inversely proportional to airflow resistance). The angle of inclination to the direction is 42. The maximum value of the above factors could be obtained before and after, and a range from 28 ° to 55 ° could be set as a range satisfying the desired condition (about 80% of the maximum value). .

In experiments to determine the relationship between the fin pitch and the factors described above, The fin pitch between the bent portion contacting one of the tube elements and the next bent portion contacting the one tube element can obtain the maximum value of the above factor at about 3.8 mm, and The desired condition can be satisfied in the range of about 3.0 mm or more and 5.0 mm or less, and the fin height can obtain the maximum value of the above factor in about 7.5 mm and about 5.0 mm. The desired condition can be satisfied within the range of m or more and 9.5 mm or less. Further, it is desirable to set the fin height so that the interval between the tube elements is formed corresponding to the fin height.

Further, in forming the louver, it is desirable that 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. Preferably, the thickness of the corrugated fin is 0.09 mm or more and 0.2 mm or less.

The above conditions are satisfied when the heat exchanger includes 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 a corrugate disposed between the tube element. The present invention can be applied to the case of a stacked heat exchanger formed by alternately stacking fins.

Further, in the laminated heat exchanger, the tube element may include a pair of upper tank portions formed at one longitudinal end, a pair of lower tank portions formed at the other longitudinal end, and one of the upper tank portions. A double-tank heat exchanger having a first refrigerant passage communicating with one of the lower tank portions and a second refrigerant passage communicating with the other of the upper tank portion and the other of the lower ink portion may be provided. Further, the tube element may be a single-tank heat exchanger having a pair of tank portions formed at one end in the longitudinal direction and a U-shaped passage communicating the pair of tank portions. BRIEF DESCRIPTION OF THE FIGURES

(A) of FIG. 1 is a front view showing a heat exchanger according to an embodiment of the present invention, which is a one-tank stacked heat exchanger, and (b) of FIG. 1 is a side view thereof. FIG. 2 (a) is a front view showing the fin height Fh of the fin, FIG. 2 (b) is a cross-sectional view thereof, and FIG. 3 is the fin lever angle. FIG. 4 is a schematic side view showing the fin pitch Fp, the fin height Fp, and the distance Dr between the end of the lever and the top of the vent. Fig. 5 is a characteristic diagram showing the relationship between the louver angle Ra and the heat exchanger capacity Fa, and Fig. 6 is a graph showing the relationship between the fin pitch Fp and the heat exchanger capacity Fa. FIG. 7 is a characteristic diagram showing a relationship between the fin height Fh and the heat exchanger capacity Fa, and FIG. 8 is a ventilation direction of the heat exchanger. Width Cw and heat exchanger capacity F a A characteristic diagram showing the relationship, FIG. 9 is a heat exchanger according to the embodiment of the present invention, is a perspective view showing a laminated heat exchanger of the two-tank. BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

The heat exchanger 1 shown in FIGS. 1 (a) and 1 (b) is a one-tank laminated heat exchanger, and includes a pair of tank portions 2 and 2 formed at one longitudinal end, and the pair of tank portions. It is composed of a plurality of tube elements 4 each including a refrigerant passage portion 3 communicating with each other, and a corrugated fin 5 disposed between the refrigerant passage portions 3 of the tube element 4. In the heat exchanger 1 shown in FIGS. 1 (a) and 1 (b), end plates 6 and 6 are disposed at both ends of the tube element 4 and the fin 5 in the stacking direction, and are located substantially at the center in the stacking direction. The tube element 4 ′ is formed by connecting the tank portion 2 in the laminating direction. It has a blind tank section 2 'that divides one of the pair of tank groups 7, 7 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) is formed extending from the tank portion 2 along the direction of air flow. At the approximate center of the evening block 7B, an outlet-side mounting portion 9 for mounting a refrigerant outflow pipe (not shown) is formed extending from the tank portion 2 along the direction of air flow. O

As a result, 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 into the tank group 7 on the other side, and flows through the tank group 7. Moving. Then, the refrigerant having 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. It is.

In the heat exchanger 1 with the above configuration, the width Cw in the ventilation direction is within the range of 30 mm or more and 57 mm or less in order to save the space of the air conditioner itself and the space of the vehicle itself. It is desired to be formed. And, in the present embodiment, the width C w of the heat exchanger 1 is formed as 40 mm. As shown in FIGS. 2 to 4, the fins 5 are connected to the vent portions 1 la and 11 b which are in contact with the refrigerant flow path portion 3 of the tube element 4 and to one of the tube elements 4. It has a flat portion 12 located between the contacting vent portion 11a and the vent portion 11b contacting the other tube element 4, and corresponds to a portion between the refrigerant flow passage portions 3 of the adjacent tube elements 4. It has a predetermined fin height Fh and a fin bit Fp between the vertices of the vent portion 11a to be in contact with the one tube element 4. Further, the fin 5 is formed with a plurality of loopers 10 extending vertically in the ventilation direction, which are cut and raised in order in the ventilation direction, and the air passing along the fins 5 is transmitted to the looper 10. The fins 5 can pass along the fins 5 so as to intersect, so increasing the inclination angle (louver angle) Ra of the louver with respect to the flat portion 12 of the fins 5 can increase the heat exchange capacity. On the other hand, if the angle Ra is increased, the ventilation resistance is increased and the heat exchange capacity is reduced.

Based on the above, in a heat exchanger with a width of 40 mm in the ventilation direction, experiments were performed with varying the roof angle Ra, and the factors indicating the cooling performance and the factors indicating the ventilation resistance were determined.From these factors, The 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.

The characteristic diagram showing the relationship between the louver angle Ra and the heat exchanger capacity F a obtained by the experiment is shown in Fig. 5, and the maximum value is obtained when the louver angle Ra is approximately 42 °. It turns out that it becomes ability. Then, the range where the maximum capacity is 80% or more when the maximum capacity is 100% is defined as an appropriate range Ras of the louver angle Ra. The proper range Ras is in the range from 28 ° to 55 ° according to the characteristic diagram shown in FIG.

Similarly, the relationship between the fin pitch Fp and the heat exchanger capacity Fa obtained by an experiment is shown in FIG. 6, in which the fin pitch Fp is about 4.0 mm. It can be seen that the maximum capacity is obtained at the time. Assuming that the range in which the heat exchanger capacity Fa is 80% or more of the maximum is the appropriate range Fps of the fine pitch Fp, as in the case described above, the appropriate range Fps is as shown in FIG. According to the characteristic diagram shown by, it is 3.0 mm or more and 5.0 mm or less.

Further, the relationship between the fin height F h and the heat exchanger capacity F a was tested. Fig. 7 shows that the maximum capacity is obtained when the fin height Fh is about 7.5 mm. Assuming that the range where 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 as shown in Fig. 6. According to the characteristic diagram, it becomes 5.0mm or more and 9.5mm 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.

Further, the fin plate thickness Ft is preferably as thin as possible in a cost-like manner. However, in order to increase the fin strength, the fin plate thickness Ft needs to be more than a predetermined value. It is desirable to set it within the range of 09 mm or more and 0.2 mm or less. Further, the distance D r between the end of the louver 10 formed in the fin 5 and the top of the fin vents 11 a and 11 b is not less than 0.2 mm and not more than 1.5 mm It is desirable. By setting the distance Dr in this range, the drainage of the fin can be improved and the fin strength when the fin is formed in a corrugated shape can be maintained. Further, the joining property by brazing between the fin 5 and the tube element 4 can be improved.

As described above, in the heat exchanger 1, the width Cw in the ventilation direction was set to 40 mm, but as shown in Fig. 8, the width in the ventilation direction was within the range of 30 mm to 57 mm. With the heat exchanger set to, 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 fin 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 includes a pair of upper tank portions 31 and 32 formed at one longitudinal end and a pair of lower tank portions 33 and 3 formed at the other longitudinal end. 4, a first refrigerant flow path 35 communicating between one upper tank section 31 and one lower ink section 33, and a first refrigerant path 35 communicating with the other upper tank section 32 and the other lower tank section. A plurality of tube elements 37 having a second refrigerant flow path 36 are provided, and the fins 5 satisfying the above-described conditions are arranged between the tube elements 37. Thus, 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 numerals 44 are end plates disposed at both ends in the stacking direction. The heat exchanger 30 is composed of four tank groups 38, 39, 40, 41 each having the tank sections 31, 32, 33, 34 communicating with each other in the stacking direction. It has. A refrigerant inlet pipe 42 is connected to a first tank group 38 composed of one upper tank part 31 and a refrigerant outlet pipe is connected to a fourth sunset group 41 composed of the other upper tank part 32. 4 3 is communicated. A second tank group 39 composed of one lower tank part 33 and a third tank group 40 composed of the other lower tank part 34 are formed at the end of the second tank group 39. The opening 45, the bypass flow path 44, and the opening 46 formed at the end of the third tank group 40 communicate with each other.

With the above configuration, the refrigerant flowing from the refrigerant inlet pipe 42 flows from the first tank group 38 to the first refrigerant flow path 35, flows to the second tank group 39, and flows into the bypass flow path. It flows into the third tank group 40 via the section 44, passes through the second refrigerant flow path 35, flows into the fourth tank group 41, and flows out from the refrigerant outlet pipe 43. Is what it is. Industrial applicability

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 louver angle is set to 28 ° or more and 55 ° or less. Depending on the fin pitch, 3.0 mm or more Since the capacity of the heat exchanger can be maintained at a predetermined level or more even when the thickness is 0 mm or less, the drainage of the fins can be improved while maintaining the performance of the heat exchanger.

Claims

The scope of the claims

1. At least a tube element through which a refrigerant flows and a corrugated fin disposed between the tube elements, wherein the corrugated fin is applied to one of the tube elements and a vent portion in contact with the tube element. A flat portion is provided between the vent portion in contact with the vent portion and the vent portion in contact with the other tube element, and the flat portion has a plurality of louvers extending in a direction perpendicular to the ventilation direction. , In a heat exchanger formed in order 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,

A heat exchanger characterized in that the inclination angle of the chamber with respect to the ventilation direction is in the range of 28 ° to 55 °.

2. In each of the corrugated fins, the fine pitch between the bent portion in contact with one tube element and the next bent portion in contact with one tube element is approximately 3.0 mm or more and 5.0 or more. 2. The heat exchanger according to claim 1, wherein the diameter is not more than mm.

3. In each of the corrugated fins, the fin height is formed in a range of approximately 5.0 mm or more and 9.5 mm or less, and the interval between the tube elements is set corresponding to the fin height. 3. The heat exchanger according to claim 1, wherein the heat exchanger is formed.

4. The distance between the end of the louver and the tube element is within a range of approximately 0.2 mm or more and 1.5 mm or less. The heat exchanger according to item 3.

5. The method according to any one of claims 1 to 4, wherein the plate thickness of the corrugated fin is not less than 0.09111111 and not more than 0.2 mm. The heat exchanger as described.

6. The heat exchanger includes a tube element having a pair of ink tanks formed at at least one end in the longitudinal direction and a refrigerant passage communicating with the tank, and a corrugated fin arranged between the tube elements. 6. 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 the heat exchangers.

7.The tube element includes 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 therewith and a second refrigerant passage communicating the other of the upper tank portion and the other of the lower tank portion. The heat exchanger according to the item.

8. The tube element is a single-tank heat exchanger having a pair of neck portions formed at one longitudinal end and a U-shaped passage communicating the pair of tank portions. 7. The heat exchanger according to item 6, wherein