Heat exchanger core

Abstract

A corrugated fin heat exchanger is provided in which the direction in which louvers are cut and raised is inclined in one direction only, and in which heat transfer performance is improved above that of conventional fins. To accomplish this, the relationship H>Qup/(Qup1)H is satisfied. H represents the core height of the heat exchanger, Qup represents the ratio of the amount of heat exchanged per corrugation between one-directional louver fins and multi-directional louver fins in an airflow part, and H represents the amount of increase in a heat transfer reduction region of a heat exchanger core as a result of changing from multi-directional louver fins to one-directional louver fins.

Claims

1. A corrugated fin heat exchanger comprising a core and two tanks, wherein the core comprises a plurality of mutually parallel elongated tins and flat tubes, the flat tubes and the tins alternating with respect to each other, the tubes being configured for flow of a first fluid therethrough and the fins being configured for flow of a second fluid along the length of the fins from a first lengthwise end of the fins proximate a first lengthwise end of the core to a second lengthwise end of the fins proximate a second lengthwise end of the core and in contact with outer faces of the tubes, wherein the fins comprise one-directional louvers in the form of fin portions each cut out from a fire and the louvers being inclined in a same direction, wherein each of the two tanks is at a respective one of the ends of the core and end portions of the tubes pass through the tanks, and wherein an angle facing the first end of the core at which the louvers are inclined from the fins, W, and H are set to satisfy the inequation (1):
H>Qup/(Qup1)H(1) wherein,
Qup=Qup(W,)=(W)+(W,)+1(2),
(W)=/(W)(3),
(W,)=/(W.Math.tan.sup.2 2)(4),
H=H(W,)=j.Math.W(sin +k.Math.sin.sup.2 )(5),
=0.3553 (mm),
=0.5447 (mm),
j=0.1419,
k=4.2789, and are regression analysis coefficients, is louver angle, (W) represents an effect of a greater of number of louvers oriented in a single direction in the core having one-directional louvers than in a core having two-directional louvers due to the absence of a multidirectional louver in t core having one-directional louvers, which, in a core having two-directional louvers, is interposed between sets of the louvers oriented in respective different directions, (W,) represents an effect of absence, in the core having one-directional louvers, of a stagnant region which, in a core having two-directional louvers, occurs in a region immediately downstream from the multidirectional louver, H is a distance in mm between the two tanks, which is the actual height of the core, H is the difference (H.sub.2H.sub.1) between effective core height (H.sub.1) of the corrugated fin heat exchanger having one-directional louvers and an actual core height and a corrugated fin heat exchanger having a same actual core height H but having multi-directional louvers wherein the fins comprise respective sets of louvers inclined in opposite directions, Qup is a ratio of an amount of heat exchanged per corrugation of the corrugated heat exchanger having one-directional louvers and the amount of heat exchanged per corrugation of the corrugated heat exchanger having multi-directional louvers, and W is an aggregate width in mm of the louvers.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) FIG. 1 illustrates comparison between an air flow by fins of the present invention and that by fins of the conventional-type heat exchanger.

(2) FIG. 2(A) illustrates a flow state of airflow of the present invention. FIG. 2(B) illustrates a flow state of airflow of the conventional-type heat exchanger.

(3) FIG. 3(A) illustrates cutting and raising of louvers of a heat exchanger core of the present invention. FIG. 3(B) illustrates cutting and raising of louvers of a conventional-type heat exchanger.

(4) FIG. 4 illustrates experimental data in which the cutting and raising louver width W is set along a lateral axis, and a rate of a heat transfer ratio in a main heat transfer region (air-flow portion) between the core of the present invention and the conventional-type core is set along a vertical axis.

(5) FIG. 5 is a graph in which the cutting and raising louver width W is set along a lateral axis, and an increased amount H of the heat transfer reduction region (air-flow reduced region) of the core of the present invention, with respect to that of the conventional-type core, is set along a vertical axis.

(6) FIG. 6 is a graph in which the cutting and raising louver width W is set along a lateral axis, and a lowest limit of a core height having effects of the core of the present invention, with respect to that of the conventional-type core, is set along a vertical axis.

(7) FIG. 7 is a graph in which the cutting and raising louver width W is set along a lateral axis, and a rate of a heat exchange amount between the heat exchanger core of the present invention and that of the conventional-type heat exchanger core.

DETAILED DESCRIPTION OF THE INVENTION

(8) Subsequently, with reference to figures, an embodiment of the present invention will be described.

(9) FIGS. 1 to 3 illustrate comparisons between the heat exchanger core of the present invention and that of the conventional type that is currently practically used, respectively.

(10) FIG. 1 is a vertical sectional view of the heat exchanger core. Further, FIG. 2(A) illustrates a flow passage of the air with the louvers of the present invention. FIG. 2(B) illustrates a flow passage of the air with the conventional-type core. FIGS. 3(A) and 3(B) illustrate a cut and raised state of each louver, respectively.

(11) The heat exchanger core of the present invention is formed with a core in which flat tubes and corrugated fins are alternately aligned in parallel. In this example, a pair of tanks 3 are disposed above and below the core, and both ends of the flat tube pass through the tanks 3. In FIG. 1, the core height H is a separation distance between the pair of tanks 3 above and below the core (height of the space portion between the pair of tanks 3). The cutting and raising louver width W of the core is shorter than the width of the core illustrated in FIG. 3 by a length of flat portions of the fin.

(12) In this example, as illustrated in FIGS. 2(A) and 3(A), the only one-directional fins are inclined as the corrugated fin, and cut and raised with the same pitch in the area of the cutting and raising width W of the louver. Further, at the both sides of the cutting and raising louver width W, a flat portion 6d is provided, and a half louver 6c is formed at the flat portion 6d. The width of the half louver 6c is as half as that of the louvers 6 other than the half louver 6c.

(13) As illustrated in FIG. 2(A), upon airflow 1 coming into a one-directional fin 7, the airflow 1 is guided into each louver 6 of the one-directional fin, so that a flow passage 4 in one direction is formed in an oblique-band-like shape from an upstream side to a downstream side.

(14) On the other hand, as illustrated in FIGS. 2(B) and 3(B), a conventional-type fin 8 includes a multi-directional louver 6b at a center of the fin in a width direction. At both sides of the multi-directional louver 6b, the louvers 6a having different directions from each other are aligned in parallel. At the both sides of the multi-directional louver 6b, a half louver is cut and raised.

(15) Upon the airflow 1 coming into the conventional-type fin 8, as illustrated in FIG. 2(B), a flow passage 5 of the conventional-type fin is formed in a mountain-like shape.

(16) As described above, the one-directional fin 7 that is an object of the present invention is totally different from the conventional-type fin 8 just like between the flow passage 4 of the one-directional fin and the flow passage 5 of the conventional-type fin.

(17) That is based on configurational difference between the one-directional fin 7 of the present invention and conventional-type fin 8. Therefore, following differences are generated.

(18) First of all, the one-directional fin 7 can have more louvers 6 compared to the conventional-type fin 8. This is because, in place of the multi-directional louver 6b of the conventional-type fin 8, the one-directional louver can be cut and raised. At this point, the core of the present invention improves a heat transfer ratio.

(19) Subsequently, it is difficult to completely convert a direction of the airflow 1 with the multi-directional louvers 6b. The conventional-type fin 8 generates a stagnant region right after a direction-converting portion in a downstream direction, but the present invention does not generate the stagnant region. At this point also, the heat transfer ratio is improved.

(20) As illustrated in FIG. 1, the airflow 1 flowing in from a left side, with the one-directional fin 7, flows in the heat exchanger core 2 obliquely within an area of an effective core height H.sub.1.

(21) On the other hand, in a case of the conventional-type fin 8, the airflow 1 flows in the heat exchanger core 2 as illustrated with a dotted line in a mountain-like shape within an area of the effective core height H.sub.2 of the conventional-type. As clearly illustrated in FIG. 1, the effective core height H.sub.2 of the conventional-type is higher than the effective core height H.sub.1 of the one-directional fin of the present invention. Therefore, in FIG. 1, one-directional fin is adopted to generate the increase H of the air-flow reduced region in the present invention. Thus, in the region of H, the heat transfer ratio is lowered.

(22) First of all, the present inventor experimentally obtains the heat transfer ratio at the effective core height H.sub.1 of the one-directional fin illustrated in FIG. 1 as a rate relative to the conventional-type fin 8. FIG. 4 illustrates the experimental data. The cutting and raising louver width W is set along a lateral axis, and the rate of the heat transfer ratio is set along a vertical axis. Each experiment is attempted at 20 degrees, 30 degrees, and 40 degrees of a louver angle.

(23) As clearly illustrated in FIG. 4, within the area of the effective core height H.sub.1 at any angle, the rate of the heat transfer ratio higher than that of the conventional-type louver is indicated.

(24) Further, FIG. 7 indicates the rate between the cutting and raising louver width W and the amount of the heat exchange in an entire core.

(25) The data is regression-analyzed, and
Qup=Qup(W,)=(W)+(W,)+1
are obtained.

(26) Herein,
(W)=/(W), and =0.3553 (mm)
are to be satisfied. Further,
(W,)=/(W.Math.tan.sup.2 2), and =0.5447 (mm)
are to be satisfied.

(27) (W) represents an effect of increase of the number of louvers. (W,) represents an effect of disappearance of the stagnant region in the downstream side of the direction-converting portion.

(28) Further,
Qup=(amount of the heat exchange per one corrugation of one-directional fins in the airflow portion)/(amount of the heat exchange per one corrugation of conventional-type fins in the airflow portion)
is to be satisfied.

(29) Subsequently, as illustrated in FIG. 1, the present inventor experimentally confirms, by adopting one-directional fins, a region H to be lost relative to the effective height H.sub.2 of the conventional-type fin. FIG. 5 illustrates the data. In FIG. 5, the lateral axis expresses the cutting and raising louver width W of the core, and the vertical axis expresses the increased amount H of the heat transfer reduction region by adopting the one-directional louver, and an each unit is mm.

(30) Based on a flowing line by numeral-value calculation, the regression analysis is performed at each louver angle , and a regression equation (5)
H=H(W,)=j.Math.W.Math.(sin +k.Math.sin.sup.2 )
(j=0.1419, k=4.2789)
are obtained.

(31) Here, considering by comparing the advantage and the disadvantage between the one-directional louver and the conventional-type fin, the area in which the effects can be obtained is expressed as
Qup(HH)/H>1.

(32) The above described equation is modified, and
H>Qup/(Qup1)H
is obtained.

(33) FIG. 6 illustrates the lowest limit (curve lines a3 to c3) of the effective height of the core of the one-directional louver obtained from the inequation.

(34) As an example, in a case of the louver angle of 20 degrees, a value of the lowest limit for the cutting and raising width W of the louver is found on the curve line a3.

(35) As long as the height of the core is kept to be the lowest limit value or more, the performance of the heat exchange higher than that of the conventional-type core can be obtained.

(36) In a case of the louver angle of 30 degrees and 40 degrees, the higher performance is also obtained.

(37) Therefore, in the heat exchanger core of one-directional louver, the H, W and may be set to satisfy
H>Qup/(Qup1)H.(1)

(38) Note that, according to the present invention, the cutting and raising louver width W is 6 to 46 mm, the cutting and raising louver angle is 20 degrees to 35 degrees, the pitch between the louvers is 0.5 to 1.5 mm, and the pitch between the fins is 2 to 5 mm. They are obtained based on discussion in which the airflow is adopted as the fluid and a flow speed at a front face of the core is set to 2 to 8 m/s.

(39) The more preferable adopting condition is that the cutting and raising louver width W is 6 to 26 mm, the cutting and raising louver angle is 20 degrees to 30 degrees, the pitch between the louvers is 0.5 to 1.0 mm, and the pitch between the fins is 2 to 3 mm. The airflow is adopted as the fluid, and the flow speed at the front face of the core is set to 4 to 8 m/s.

REFERENCE SIGNS LIST

(40) 1 airflow 1a airflow 2 heat exchanger core 3 tank 4 flow passage of one-directional fin 5 flow passage of conventional-type fin 6 louver 6a louver 6b multi-directional louver 6c half louver 6d flat portion 7 one-directional fin 8 conventional-type fin H core height W cutting and raising louver width cutting and raising louver angle