JPH10185359A - Finned heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the flow passage area of refrigerant and increase a flow rate to improve heat transfer rate remarkably by a method wherein the path of a heat transfer tube is designed so as to be two paths at the inlet port unit of refrigerant while the specified part of whole of the heat transfer tube is designed so as to be one path near the outlet port of the refrigerant upon condensing operation. SOLUTION: Upon condensing operation in a finned heat exchanger, refrigerant flows into the heat exchanger through two paths of inlet tubes 1, 2, then, is joined near a point 10 after passing through heat transfer tubes 3, 4 while the refrigerant flows through one path at the downstream of a heat transfer tube 5 and flows out through an outlet tube 6. In this case, the part of one path from the heat transfer tube 5 to the outlet tube 6 is provided at the upstream side with respect to the inflow direction A of air while the heat transfer tube of one path near an outlet port is designed so as to occupy 5-30% of total heat transfer tube. On the other hand, the inlet tubes 1, 2 are provided at the downstream side with respect to the inflow direction A of air while the part of one path from the heat transfer tube 5 to the outlet tube 6 is provided at upstream side with respect to the inflow direction A of the air. Further, fins 7 are divided at a dividing place B into fin units 7a, 7b in the direction of upper and lower stages while the outlet tube 6 is provided at the end of the dividing place B.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a finned heat exchanger widely used in an air conditioner or a refrigerator.

[0002]

2. Description of the Prior Art In a conventional finned heat exchanger, as shown in FIG. 11, during a condensing operation, refrigerant flows in two passes from inlet pipes 1 and 2 and flows out of outlet pipes 8 and 9 in two passes. Thereby, the flow path area of the refrigerant is increased, the pressure loss on the refrigerant side is reduced, and the performance is improved. That is, in order to suppress a decrease in the heat exchange capacity due to an increase in the refrigerant flow resistance, the refrigerant exchanges heat with the air while flowing through the inside of the heat transfer tube from the inlet to the outlet in two paths as shown by solid arrows.

[0003]

The state of the refrigerant in the heat exchanger is classified into three during the condensing operation: a superheated region, a gas-liquid two-phase region, and a supercooled region. Contributing is the gas-liquid two-phase region in which the refrigerant has latent heat of condensation. Further, supercooling is also indispensable from the viewpoint of increasing the stability of the refrigeration cycle and the refrigeration effect.

However, in the above-described two-pass heat exchanger shown in FIG. 11, the condensing temperature of the refrigerant in the heat exchanger is reduced due to the recent promotion of energy saving, and the temperature difference with the air to be heat-exchanged is very small. Therefore, when supercooling is increased, the subcooling region that hardly contributes to heat exchange increases significantly inside the heat exchanger, and the heat exchanger capacity is reduced.

Further, when the above-mentioned conventional finned heat exchanger having a refrigerant flow path as shown in FIG. 11 is used as a condenser, the condensing temperature is lowered to improve the coefficient of performance of an air conditioner or a refrigerator in particular. In order to increase the degree of supercooling, the supercooling region of the refrigerant has a heat transfer coefficient lower by about an order of magnitude than the two-phase region and has a small temperature difference with air. There has been a problem that the length of the refrigerant flowing in the supercooled state is significantly increased, and the heat exchange capacity of the entire finned heat exchanger is significantly reduced.

A conventional finned heat exchanger is disclosed in Japanese Patent Application Laid-Open No. 63-1833 shown in FIG.
As disclosed in Japanese Patent Publication No. 91, there is used a fin provided with a plurality of cutouts on both sides of the fin surface. However, because of its large ventilation resistance, the heat exchange capacity does not decrease much,
JP-A-2-2177 shown in FIG. 13 in which the ventilation resistance is greatly reduced and the heat exchange capacity for the same pneumatic power is improved.
No. 92, a finned heat exchanger having a plurality of cut-and-raised portions on one side of the fin surface, the width of which is approximately 1/3 of the distance between adjacent cut-and-raised portions in the column direction, is also used.

That is, as shown in FIG.
The heat transfer tubes 13 are inserted into the fin collars 12 burred at regular intervals, and air flows in the direction of arrow A.

The fins 11 are arranged in three rows between two adjacent heat transfer tubes 13 on one side of the fin surface.
14a, two 14b, and three 14c. The width W in the column direction of the cut-and-raised pieces in three rows
f is formed to be approximately 1/3 of the width Wb of the fin base in the column direction.

In the conventional finned heat exchanger having fins as shown in FIG. 13, a plurality of rows of heat transfer tubes are used, and the temperature difference between the refrigerant flowing inside each adjacent heat transfer tube in the row direction is reduced. At one time, for example, when the refrigerant flowing inside at least one of the heat transfer tubes is in a supercooled liquid or superheated gas state, a fin having a large flat area between the refrigerant flowing inside each heat transfer tube is provided. Heat is exchanged by heat conduction through the base. Therefore, FIG.
There is a problem that even if the fins are used in two rows, the heat exchange capacity is not effectively improved.

[0010] In order to solve the above-mentioned conventional problems, the present invention reduces the supercooling region which hardly contributes to the heat exchange capacity while taking a large amount of supercooling, so that the gas-liquid contributing to the heat exchange capacity is reduced. It is an object of the present invention to provide a finned heat exchanger in which the heat exchange capacity is greatly improved by increasing the two-phase region. The present invention also reduces the condensation temperature, does not reduce the heat exchange capacity even if the degree of subcooling is increased, and also allows the refrigerant flowing between the adjacent heat transfer tubes in the row direction to be used in a plurality of rows. It is an object of the present invention to provide a finned heat exchanger that suppresses heat conduction through a fin base and effectively improves heat exchange capacity in a plurality of rows.

[0011]

In order to solve the above-mentioned problems, in the heat exchanger with fins of the present invention, the path of the heat transfer tube has two paths at the inlet of the refrigerant during the condensation operation and one path near the outlet. Things.

When the path of the heat transfer tube is two paths at the inlet of the refrigerant during the condensing operation and one path near the outlet, the supercooled liquid refrigerant cooled by air can be changed from two paths to one path. As a result, the flow path area of the refrigerant is reduced, so that the speed is increased and the heat transfer coefficient is greatly improved. As a result, at the same degree of subcooling, the subcooling region that hardly contributes to heat exchange decreases, and the gas-liquid two-phase region that contributes to heat exchange capability can be increased.

Further, according to the present invention, by providing the one-pass portion on the upstream side with respect to the air inflow direction, the portion having the lowest temperature due to the supercooling during the condensing operation is located upstream in the air inflow direction. As a result, the temperature gradient of the refrigerant increases, and the effect is greatly improved.

The present invention also provides a superheated refrigerant which has the highest temperature during the condensing operation by providing two heat transfer tubes which are inlets of the refrigerant heat exchanger in the condensing operation on the downstream side in the air inflow direction. Is arranged downstream with respect to the air inflow direction, and the path is configured to be counter-current, so that the temperature gradient of the refrigerant is increased and the effect is greatly improved.

Further, according to the present invention, in the condensing operation, two heat transfer tubes serving as the inlet of the heat exchanger for the refrigerant are provided on the downstream side in the inflow direction of the air, and the outlet 1 path portion is adjacent to the inlet portion and upstream thereof. By providing the path on the side, the place where the temperature of the refrigerant is the highest and the place where the temperature of the refrigerant is low are disposed adjacent to each other.

Further, according to the present invention, the fins are substantially
By providing a heat transfer tube at the end of the split portion of the fin at the end of the divided portion of the fin, a heat transfer tube at the lowest temperature inside the heat exchanger and a hot transfer tube adjacent in the step direction are provided. By dividing the heat tubes by dividing the fins, heat exchange due to heat conduction through the fins of both heat transfer tubes can be prevented, and loss inside the heat exchanger can be reduced.

Further, a plurality of main cut-and-raised portions are provided on one side of the surface of the fin between the heat transfer tubes adjacent in the stepwise direction, and the width of the cut-and-raised columns in the column direction is set to the distance between the adjacent cut-and-raised portions in the column direction. When the fin is divided at least at one position between the stages, the heat transfer tubes are connected to allow the refrigerant to pass therethrough, and when used as a condenser,
The heat transfer tubes near the outlet including the final outlet of the refrigerant having a ratio of 5% to 30% of the total number of the heat transfer tubes are configured with one refrigerant flow channel, and the refrigerant flow channels of the other heat transfer tubes are configured with two, The heat transfer tubes near the outlet including the final outlet of the refrigerant having the refrigerant flow path number of 1 are arranged in the most upwind row of the air, and the heat transfer tubes at the final outlet of the refrigerant are arranged at any of the fins at the inter-stage division points. The two heat transfer tubes at the inlet of the refrigerant are arranged at the end stages, and the two heat transfer tubes at the inlet and downstream of the heat transfer tubes near the outlet including the final outlet of the refrigerant having the number of refrigerant flow paths of one are the most downstream. Insulation means are provided on the fin surface near the center between the heat transfer tubes and the heat transfer tubes adjacent to the heat transfer tubes arranged in the row in the leeward direction, at least in the state of supercooled liquid or superheated gas. According to this configuration, the refrigerant in the super-cooled liquid state flows through the heat transfer tube through the refrigerant passage. Since the number is set to 1, even if the condensing temperature is lowered and the degree of supercooling is increased, the heat transfer coefficient can be greatly improved without increasing the flow resistance of the refrigerant so much. The heat exchange by heat conduction through the fins from the heat transfer tube at the final exit of the refrigerant arranged in the stage to the heat transfer tube adjacent in the stage direction can be halved, and the refrigerant flow in which the refrigerant in the supercooled liquid state flows inside A heat transfer tube with the number of paths being 1 is arranged at the most upwind side, and two heat transfer tubes at a refrigerant inlet through which a refrigerant in a superheated gas state flows are arranged in the most downstream row of the leeward or downstream stage. Therefore, the heat exchange capacity can be improved by the counterflow effect, and the refrigerant flowing inside each heat transfer tube is provided by the heat insulating means provided at the fin portion near the center between the heat transfer tubes adjacent in the row direction. Between the fin bases And, it is possible to improve the heat exchange capacity in a plurality of rows.

Further, as heat insulating means provided at least on the surface of the fin near the center between the heat transfer tube and the heat transfer tube adjacent to the heat transfer tube in the row direction, the heat transfer tube passing at least in the state where the refrigerant is a supercooled liquid or a superheated gas. According to this configuration, it is possible to suppress heat conduction through the fin base between the refrigerant flowing inside the heat transfer tubes adjacent to each other in the row direction, and to perform cutting. The heat transfer performance can be improved by the temperature boundary layer leading edge effect of the portion.

Further, the length of the cut portion in the step direction is set to be not less than the diameter of the heat transfer tube and not more than about six times the step pitch. According to this configuration, the inside of the heat transfer tube adjacent in the row direction is formed. Heat conduction through the fin base between the flowing refrigerants can be effectively suppressed.

Further, the end of the cut portion is provided in the vicinity of the end of one of the fins on which the heat transfer tubes at the final outlet of the refrigerant are disposed, and the heat transfer tubes are arranged at the most temperature. Since there is always a cut portion between the heat transfer tube at the final outlet of the refrigerant having a low temperature and the heat transfer tube adjacent to the heat transfer tube in the row direction, heat conduction through the fin base can be suppressed most effectively.

According to the configuration in which a plurality of cut portions are continuously formed in the stepwise direction via the non-cut portions, the heat transfer performance can be further improved by the temperature boundary layer leading edge effect of the cut portions.

According to the configuration in which the cut portions are continuously connected in the step direction through the non-cut portions, the heat transfer performance can be further improved by the temperature boundary layer leading edge effect of the cut portions.

The length of the non-cut portion is set to about 1 of the diameter of the heat transfer tube.
According to the configuration of / 2 or less, heat is conducted between the refrigerant flowing inside the heat transfer tubes adjacent to each other in the row direction through the non-cut portions, and it is possible to suppress a decrease in heat exchange capacity.

The stepwise length of the cut portion and the length of the non-cut portion are mainly constant, and the total length of the finned heat exchanger in the step direction is determined by the stepwise length of the cut portion and the length of the noncut portion. When a remainder is generated that is not divisible by an integer when divided by the sum of, according to the configuration in which the length in the step direction of one cut portion is increased by a length corresponding to the remainder, cutting of a fixed length is performed. When processing fins by repeatedly using the mold of the part, it is possible to eliminate the non-cut part and form a cut part longer than the other part by shifting the fin only one place in the step direction by the length equivalent to the remainder and hitting twice. In addition, it is possible to easily obtain a finned heat exchanger in which the cutting section is continuously connected in all stages in the step direction through the non-cutting section.

According to the configuration in which the cut portion having a longer stepwise length is provided downwind of the air near the heat transfer pipe near the outlet including the final outlet of the refrigerant having one refrigerant flow path, It is possible to effectively insulate the heat transfer tubes in which the coolant in the coolant state flows inside and the heat transfer tubes adjacent in the row direction.

According to the structure in which the fins are divided in rows in the step direction as the heat insulating means, it is possible to suppress the heat conduction through the fin base between the refrigerant flowing inside the heat transfer tubes adjacent in the row direction. In addition, the heat transfer performance can be improved by the temperature boundary layer leading edge effect.

According to the structure in which the cut-and-raised portion having the same width as the main cut-and-raised portions is provided on the same side as the surface where the cut-and-raised portions are cut and raised as the heat insulating means, the heat transfer tubes adjacent in the row direction are provided. In addition to suppressing the heat transfer through the fin base between the refrigerant flowing inside the fin base, the heat transfer performance can be improved by the temperature boundary layer leading edge effect of the cut and raised, and all the cut and raised can be on the same side The maintenance of the mold is easy.

According to the structure in which the cut-and-raised portion having the same width as the main cut-and-raised portions is provided on the side opposite to the surface where the main cut-and-raised portions are cut and raised, the heat transfer tubes adjacent in the row direction are provided. Between the refrigerant flowing inside the fin base, it is possible to suppress the heat conduction, and the heat transfer performance can be improved by the cut-and-raised temperature boundary layer leading edge effect. Can be obtained by easily remodeling one in which the front and back are alternately provided.

As a heat insulating means, a cut-and-raised portion having the same width as that of the main and plural cut-and-raised portions is provided on the side opposite to the main and multiple cut-and-raised portions. In the middle between, on the side opposite to the side where the main cuts are cut,
That is, according to the configuration in which a plurality of cut-and-raised portions having the same width as the main plurality of cut-and-raised portions are provided alternately, heat conduction through the fin base is suppressed between the refrigerant flowing inside the heat transfer tubes adjacent in the row direction. The heat transfer performance can be improved by the temperature boundary layer leading edge effect of the plurality of cut-and-raised portions provided alternately on the front and back sides.

The height of the cut-and-raised portion is set to approximately 1 / fin of the fin pitch.
According to the configuration of 2 to 2/3, the velocity distribution of the air between the fins is uniform, and the rise in ventilation resistance can be reduced.

The number of cut-and-raised portions is determined by n in the order of distance from a straight line connecting the centers of heat transfer tubes adjacent in the step direction.
, N1, n2, n3,..., N1 ≦ n2 ≦ n3
According to the configuration that satisfies ≤ ..., local velocity distribution is hardly generated on the leeward side, and rise in blowing noise can be reduced.

According to the configuration in which the raised portion near the heat transfer tube is formed substantially in the direction and position along the outer periphery of the heat transfer tube, the water stop area generated in the downstream of the heat transfer tube is reduced, and the effective heat transfer area is reduced. The fin efficiency is high because the distance from the heat transfer tube to the rise of the cut-out is short, and the sum of the lengths of each cut-out is long, so it is possible to secure a larger portion of the temperature boundary layer leading edge effect. , Heat transfer performance can be increased.

According to the structure in which the rising portion of the cut-and-raised portion which is not near the heat transfer tube is formed so as to substantially follow the main flow direction of the air flowing between the fins, it has an effect of rectifying the air flow and does not increase the ventilation resistance so much. In addition, it is possible to reduce an increase in blowing noise.

[0034]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A finned heat exchanger according to each embodiment of the present invention will be described below with reference to the drawings.

FIG. 1 shows a configuration of a finned heat exchanger according to a first embodiment of the present invention. During the condensing operation, the refrigerant flows in two passes from the inlet pipes 1 and 2 respectively, flows as indicated by solid arrows, merges near the point 10 passing through the heat transfer pipes 3 and 4, and flows downstream from the heat transfer pipe 5 in one pass. And finally exits the outlet tube 6.

A portion of one path from the heat transfer tube 5 to the outlet tube 6 is provided on the upstream side with respect to the air inflow direction A. One pass heat transfer tube near the outlet is 5 to 3 of all heat transfer tubes.
Desirably, it occupies zero.

The inlet pipes 1 and 2, which are the inlets during the condensation operation, are provided on the downstream side with respect to the air inflow direction A.

In addition, the inlet pipes 1 and 2, which are the inlets during the condensation operation, are provided on the downstream side with respect to the air inflow direction A, and one path from the heat transfer pipe 5 to the outlet pipe 6 is connected to the heat exchanger. It is provided adjacent to the row direction and upstream with respect to the air inflow direction A.

Further, the fin 7 is divided into fin portions 7a and 7b in a vertical direction at a dividing point B, and an outlet pipe 6 which is a final exit of one pass portion is provided at an end of the dividing point B of the fin 7. Have been.

According to the above configuration, (1) During the condensation operation, the refrigerant is supplied from the inlets 1 and 2 through the inlets 1 and 2 respectively.
The heat flows through the heat transfer pipes 3 and 4 and merges in the vicinity of the point 10, flows downstream from the heat transfer pipe 5 in one pass, and finally flows out from the outlet pipe 6. As described above, by making one pass near the refrigerant outlet during the condensing operation, the liquid refrigerant which has been cooled by air and is in a supercooled state changes from two passes to one pass, so that the flow path area of the refrigerant is reduced. As a result, the speed of the refrigerant is increased and the heat transfer coefficient is greatly improved, and the subcooling region that hardly contributes to the heat exchange at the same degree of subcooling decreases. This makes it possible to increase the gas-liquid two-phase region that contributes to the heat exchange capacity, and can greatly improve the heat exchange capacity.

(2) By providing a portion of one path from the heat transfer tube 5 to the outlet tube 6 on the upstream side with respect to the air inflow direction A, the portion which has become low in temperature due to supercooling during the condensing operation is inflow of air. If the path is arranged in the counterflow direction with respect to the direction A, the temperature gradient of the refrigerant is increased and the effect is greatly improved.

(3) By providing two heat transfer tubes, which are the inlets of the refrigerant heat exchangers in the condensing operation, on the downstream side with respect to the inflow direction of the air, the superheated refrigerant having the highest temperature in the condensing operation can be removed from the air. In the case where the path is formed in the counterflow direction with respect to the inflow direction, the temperature gradient of the refrigerant is increased, and the effect is greatly improved.

(4) At the time of the condensation operation, the inlet pipes 1 and 2 which are the inlets of the heat exchanger of the refrigerant are provided on the downstream side with respect to the inflow direction A of the air.
Is provided adjacent to and upstream of the inlet pipes 1 and 2 so that the highest temperature and the lowest temperature of the refrigerant are disposed adjacent to each other. The gradient increases and the effect is greatly improved.

(5) The fin 7 is divided into two parts in the vertical direction at the dividing point B, and the exit pipe 6 which is the final exit of the exit 1 pass portion
Is provided at the end of the divided portion B of the fin,
By separating the fin 7 from the outlet pipe 6 having the lowest temperature inside the heat exchanger and the high-temperature heat transfer pipe 3 adjacent in the stepwise direction, heat exchange due to heat conduction of both heat transfer pipes is prevented. In addition, the loss inside the heat exchanger is reduced, and the heat transfer performance is greatly improved.

Hereinafter, finned heat exchangers according to second to sixth embodiments of the present invention will be described with reference to the drawings.

First, a configuration common to the second to sixth embodiments of the present invention will be described with reference to FIGS. FIG.
(A) is a top view which shows the structure of the fin common to the finned heat exchanger concerning 2nd thru | or 6th embodiment of this invention,
(B) is a detailed sectional view along line IXB-IXB of FIG. 9 (A).

As shown in FIG. 9, a heat transfer tube 13 is inserted into a fin collar 12 burred at regular intervals to a fin 11, and air flows in the direction of arrow A. Fins 11
Fins 11 are provided between two heat transfer tubes 13 adjacent in the step direction.
All on the same side with respect to the surface of, for example, fin collar 1
On the side opposite to 2, there is a cut-and-raised group consisting of three rows of cut-and-raised, one cut-and-raised 24a, one cut-and-raised 24b and two cut-and-raised 24c. The width Wf of the cut-and-raised three rows in the column direction is formed to be approximately １ ／ to の of the width Wb of the fin base portion in the column direction. The height h of the cut-and-raised portions 24a, 24b, 24c is formed to be approximately 1/2 to approximately 2/3 of the fin pitch Pf. The rising portions 25a, 25b, 25c of the cut-and-raised portions 24a, 24b, 24c near the heat transfer tube 13 are arranged in directions and positions substantially along the outer periphery of the heat transfer tube 13. 24
The rising portion 25d of the side c not on the side near the heat transfer tube 13
Are formed in a direction substantially along the main flow direction of the air.

FIG. 10 is a front view showing the configuration of a refrigerant passage common to the finned heat exchangers according to the second to sixth embodiments of the present invention.

As shown in FIG. 10, the fins 11 are divided into two fins 11a and 11b at a dividing point B.
When the heat exchanger with step fins is used as a condenser, the refrigerant in the superheated gas state is supplied to the heat transfer tubes 17a, 1
8a, flows while exchanging heat as indicated by the solid arrows, and begins to be almost supercooled.
After passing through b and 18b, they merge into one refrigerant flow path, flow while being further cooled from the heat transfer tubes 19a to 19b and 19c in the windward row, and flow out from the heat transfer tube 19d at the final outlet.

That is, of the 30 heat transfer tubes, the four heat transfer tubes 19a to 19d near the outlet including the final outlet of the refrigerant are constituted by one refrigerant flow passage, and the refrigerant flow passages of the other heat transfer tubes are provided. The number consists of two.

Heat transfer tube 1 near the outlet including the final outlet of the refrigerant
9a to 19d are arranged in a row on the windward side, and the heat transfer tube 19d at the final outlet of the refrigerant is arranged in a stage at the end of the interstage division point B of the fin.

Two heat transfer tubes 17a, 18a at the inlet of the refrigerant
Are arranged in the leeward stages and rows of the heat transfer tubes 19a to 19d.

A finned heat exchanger according to a second embodiment of the present invention will be described with reference to FIG.

FIG. 2 is a plan view of the fins of the finned heat exchanger according to the second embodiment of the present invention.

The cutouts 31 and 33 having almost no width or cutouts are provided in the fin surface near the central portion between the heat transfer tubes 13 adjacent in the row direction, and are long in the stepwise direction. Are formed at a diameter not less than the diameter of the heat transfer tube and at most about 5 to 6 times the step pitch. Cutting section 31,
A plurality 33 are continuously provided in the step direction through the non-cutting portion 32, and are provided continuously in all steps in the present embodiment.

Specifically, in the present embodiment, the cutting portion 31 whose sum of the length and the length of the non-cut portion 32 is twice the step pitch,
Only one cut portion 33 is formed, which is mainly formed, and is longer than the cut portion 31 by a length corresponding to the remainder of one step obtained by dividing 15 steps by two. That is, the sum of the length of the cutting portion 33 and the length of the non-cutting portion 32 is three times the step pitch.

The end portion 34 of the cutting portion 33 is provided near the end portion B of the fin where the heat transfer tube 19d at the final outlet of the refrigerant is disposed.

The cutting portion 33 longer than the cutting portion 31 is provided downstream of the heat transfer tubes 19a to 19d from the outlet including the final outlet of the refrigerant having one refrigerant flow path.

A finned heat exchanger according to a third embodiment of the present invention will be described with reference to FIG.

FIG. 3 is a plan view of the fins of the finned heat exchanger according to the third embodiment of the present invention.

The fins are arranged between the rows 35 over the entire length in the step direction.
Is divided.

A finned heat exchanger according to the fourth and fifth embodiments of the present invention will be described with reference to FIGS.

FIG. 4 is a plan view of the fins of the finned heat exchanger according to the fourth and fifth embodiments of the present invention.
FIG. 5A is a detailed plan view of the fins of the finned heat exchanger according to the fourth embodiment of the present invention, and FIG. 5B is a plan view of FIG.
6A is a cross-sectional view taken along line VB-VB, FIG. 6A is a detailed plan view of a fin of the heat exchanger with fins according to the fifth embodiment of the present invention, and FIG. It is sectional drawing which follows a VIB line.

First, a finned heat exchanger according to a fourth embodiment will be described. The two cut-and-raised portions 36 whose height h is approximately 1/2 to approximately 2/3 of the fin pitch are formed in a row adjacent to the heat transfer tube 13 in which the refrigerant passes through in the state of a supercooled liquid or a superheated gas. On the surface of the fin 11 near the center between the heat tubes 13, a plurality of main cut-and-raised portions 24 a,
The same width Wf as the cut and raised portions 24a, 24b and 24c is provided on the same side where the cut and raised portions 24b and 24c are formed. The rising portion 37 c of the cut-and-raised portion 36 on the side near the heat transfer tube 13 is arranged in a direction and position substantially along the outer periphery of the heat transfer tube 13. 36 heat transfer tubes 1
The rising portion 37d on the side other than the vicinity of 3 is formed in a direction substantially along the main flow direction of air.

Next, a finned heat exchanger according to a fifth embodiment will be described. The two cut-and-raised portions 38 whose height h is approximately １ ／ to approximately ／ of the fin pitch are formed in a row adjacent to the heat transfer tube 13 in which the refrigerant passes through in the state of a supercooled liquid or a superheated gas. On the surface of the fin 11 near the center between the heat tubes 13, a plurality of main cut-and-raised portions 24 a,
On the side opposite to where the cuts 24b and 24c are cut and raised, they are provided with the same width Wf as the cut and raised 24a, 24b and 24c. The rising portion 39 c of the cut-and-raised portion 38 on the side near the heat transfer tube 13 is arranged in a direction and position substantially along the outer periphery of the heat transfer tube 13. 38 heat transfer tubes 1
The rising portion 39d on the side other than the side near 3 is formed in a direction substantially along the main flow direction of the air.

A finned heat exchanger according to a sixth embodiment of the present invention will be described with reference to FIGS.

FIG. 7 is a plan view of the fins of the finned heat exchanger according to the sixth embodiment of the present invention. FIG. 8A is a plan view of the fins of the finned heat exchanger according to the sixth embodiment of the present invention. FIG. 8 (B) is a detailed plan view, and FIG.
It is sectional drawing which follows the B line.

The height h is approximately 1/2 to approximately 2/3 of the fin pitch.
4b, two cut-and-raised portions 44c are provided on the surface of the fin 11 near the heat transfer tube 13 through which the refrigerant passes through in a state of supercooled liquid or superheated gas.
a, 24b, and 24c are provided on the opposite side of the cut and raised portions, in the centers of the cut and raised portions 24a, 24b, and 24c, that is, alternately on the front and back sides, with the same width Wf as the cut and raised portions 24a, 24b, and 24c. is there. Cut and raise 44
The rising portions 45a, 45b, 45c of the a, 44b, 44c near the heat transfer tube 13 are arranged in directions and positions substantially along the outer periphery of the heat transfer tube 13. The rising portion 45d of the cut-and-raised portion 44c on the side other than the side near the heat transfer tube 13 is formed in a direction substantially along the main flow direction of air.

The surface of the fin 11 of the heat exchanger with fins according to the fourth to sixth embodiments is cut and raised 36,
The coolants 38, 44a, 44b, and 44c can be used not only in the vicinity of the heat transfer tube 13 through which the refrigerant passes through in a state of supercooled liquid or superheated gas, but also in all areas.

According to the above configuration, (1) a plurality of cut-and-raised portions 24a, 24 on only one side of the surface of the fin 11 between the heat transfer tubes 13 adjacent in the step direction.
b, 24c, and cut and raised 24a, 24b, 24c
The width Wf in the column direction is set to approximately 1/3 to 1/2 of the distance Wb between two cut-and-raised portions adjacent in the column direction, and the fins are divided at least at one portion between the stages B, and the heat transfer tubes 13 are formed. When used as a condenser and configured to allow the refrigerant to pass through and communicate with the interior, the refrigerant flows through the heat transfer tubes 19a to 19d near the outlets including the final outlet of the refrigerant at a ratio of 5% to 30% of the total number of heat transfer tubes. The number of paths is one, the number of refrigerant flow paths of the other heat transfer tubes is two, and the heat transfer tubes 19a to 19d near the outlet including the final outlet of the refrigerant having the number of refrigerant flow paths of one are the most airflow. The heat transfer tubes 19d at the final outlet of the refrigerant are arranged in the upper row, and the heat transfer tubes 19d at the end of one of the inter-stage division portions of the fins are arranged at the ends of the heat transfer tubes 17a, 18a at the inlet of the refrigerant. Heat transfer tubes 19a to 1 near the outlet including the final outlet of the refrigerant having one path
A heat transfer tube 13 and a heat transfer tube 13 that are arranged in the most leeward row of a leeward or near leeward stage of 9d air, and in which at least a refrigerant passes through the inside in a supercooled liquid or superheated gas state.
Insulation means is provided on the surface of the fin 11 near the center between the heat transfer tubes 13 adjacent to each other in the row direction. Since the number of paths is 1, even if the condensing temperature is lowered and the degree of subcooling is increased, the heat transfer coefficient can be greatly improved without increasing the flow resistance of the refrigerant so much. The heat exchange by heat conduction through the fins from the heat transfer tube 19d at the final outlet of the refrigerant disposed in the stage of the part B to the adjacent heat transfer tube in the stage direction can be halved, and the refrigerant in a supercooled liquid state is formed inside. Heat transfer tubes 19a to 19 with the number of flowing refrigerant channels as one
d is arranged at the most leeward side, and two heat transfer tubes 17a, 18a at the refrigerant inlet through which the refrigerant in the superheated gas state flows are arranged in the most downstream row of the leeward or the stage near the leeward. The heat exchange capacity can be improved by a natural effect, and a heat insulating means provided in the fin 11 near the center between the heat transfer tubes 13 adjacent in the row direction allows heat exchange between the refrigerant flowing inside each heat transfer tube 13. Thus, heat conduction through the fin base can be suppressed, and the heat exchange capacity in a plurality of rows can be improved.

(2) As the heat insulating means, the cut portions 31 and 33 long in the step direction are provided. According to this configuration, the refrigerant flowing through the inside 13 of the heat transfer tube adjacent in the column direction passes through the fin base. In addition to suppressing heat conduction, the heat transfer performance can be improved by the temperature boundary layer leading edge effect of the cut portions 31 and 33.

(3) The length of the cut portions 31 and 33 in the step direction is not less than the diameter of the heat transfer tube and not more than 5 to 6 times the step pitch. Heat conduction through the fin base between the refrigerant flowing inside the heat transfer tube 13 can be effectively suppressed.

(4) The end portion 34 of the cutting portion 33 is provided in the vicinity of any interstage division B of the fin 11 in which the heat transfer tube 19d at the final outlet of the refrigerant is arranged. Between the heat transfer tube 19d at the final outlet of the refrigerant having the lowest temperature and the heat transfer tube 13 adjacent thereto in the row direction.
Since there is always 1, 33, heat conduction through the fin base can be suppressed most effectively.

(5) The cutting sections 31 and 33 are
According to this configuration, the heat transfer performance can be further improved due to the temperature boundary layer leading edge effect of the cut portions 31 and 33.

(6) The cutting sections 31 and 33 are
According to this configuration, the heat transfer performance can be further improved due to the temperature boundary layer leading edge effect of the cut portions 31 and 33.

(7) The length of the non-cut portion 32 is set to be approximately １ ／ or less of the diameter of the heat transfer tube 13.
Heat is conducted between the refrigerant flowing inside the heat transfer tubes 13 adjacent to each other in the column direction through the non-cut portions 32, so that a decrease in heat exchange capacity can be suppressed.

(8) The stepwise length of the cut portion 31 and the length of the non-cut portion 32 are mainly constant, and the total length of the finned heat exchanger in the stepwise direction is equal to the stepwise length of the cut portion. When a remainder is generated that is not divisible by an integer when divided by the sum of the lengths of the cut portions, the length of one cut portion 33 in the step direction is increased by a length corresponding to the remainder. According to the configuration, even when the fin is machined by repeatedly using the mold of the cut portion 31 having a fixed length, the non-cut portion is hit twice by shifting the fin by one position in the step direction by a length corresponding to the remainder. By forming the cut portion 33 longer than the other cut portion, it is possible to easily obtain a finned heat exchanger in which the cut portions 31 and 33 are continuously connected in the step direction through the non-cut portion 32 in all stages.

(9) The longer cut portion 33 is provided downstream of the air near the heat transfer tubes 19a to 19d near the outlet including the final outlet of the refrigerant having one refrigerant flow path.
According to this configuration, the heat transfer tubes 19a to 19d through which the refrigerant in the supercooled liquid state flows inside and the heat transfer tubes 13 adjacent in the row direction
Can be effectively insulated.

(10) As the heat insulating means, the fins are divided along the entire length in the stepwise direction at intervals between the rows 35. According to this configuration, the fin base is interposed between the refrigerant flowing inside the heat transfer tubes 13 adjacent in the row direction. And the heat transfer performance can be improved by the temperature boundary layer leading edge effect.

(11) As the heat insulating means, the main pluralities of the cut-and-raised parts 24a, 24b, and 24c are provided on the same side as the plane on which the plural plural cut-and-raised parts 24a, 24b, and 24c are formed.
The cut-and-raised portion 36 having the same width Wf as that of the b and 24c is provided. According to this configuration, heat conduction through the fin base is suppressed between the refrigerant flowing inside the heat transfer tubes 13 adjacent in the row direction. And the heat transfer performance can be improved by the temperature boundary layer leading edge effect of the cut-and-raised portions 36, and all the cut-and-raised portions 24a, 24b, 24c, and 3
Since 6 is provided on the same side, maintenance of the mold is easy.

(12) As a heat insulating means, a plurality of main cut-and-raised portions 24a, 24a, 24c are provided on the side opposite to a surface where the main plurality of cut-and-raised portions 24a, 24b, 24c are cut and raised.
The cut-and-raised portion 38 having the same width Wf as that of the b and 24c is provided. According to this configuration, it is possible to suppress heat conduction through the fin base between the refrigerant flowing inside the heat transfer tubes 13 adjacent in the row direction. The heat transfer performance can be improved by the temperature boundary layer leading edge effect of the cut-and-raised portion 38, and the mold can be obtained by easily remodeling a die having a plurality of cut-and-raised portions alternately provided on both sides. be able to.

(13) As a heat insulating means, the main pluralities of the cut-and-raised parts 24a, 24b and 24c are provided on the side opposite to the side where the plural plural cut-and-raised parts are cut and raised.
b, 24c are provided with cut-and-raised portions 44c having the same width Wf, and a plurality of cut-and-raised portions 24c adjacent in the column direction are provided.
a, 24b, 24c, the same width as the main plurality of cut-and-raised parts 24a, 24b, 24c, on the opposite side to the surface where the main cut-and-raised parts 24a, 24b, 24c are cut, ie, alternately front and back. A plurality of cut-and-raised portions 44a and 44b of Wf are provided. According to this configuration,
Between the refrigerant flowing inside the heat transfer tubes 13 adjacent in the row direction,
Heat conduction through the fin base can be suppressed, and a plurality of cut-and-raised portions 24 provided alternately on the front and back sides
The heat transfer performance can be improved by the temperature boundary layer leading edge effect of a, 24b, 24c, 44a, 44b, 44c.

(14) Cutting and raising 24a, 24b, 24
The height h of c, 36, 38, 44a, 44b, 44c is approximately 1/2 to approximately 2/3 of the fin pitch Pf. According to this configuration, the velocity distribution of air between the fins is uniform. Thus, an increase in ventilation resistance can be reduced.

(15) Each cutting and raising 24a, 24b, 2
When the numbers of 4c, 36, 38, 44a, 44b, 44c are n1, n2, n3,... In ascending order from a straight line connecting the centers of the heat transfer tubes adjacent in the step direction,
n1 ≦ n2 ≦ n3 ≦... According to this configuration, a local velocity distribution is hardly generated on the leeward side, and an increase in blowing noise can be reduced.

(16) Cutting and raising 24a, 24b, 24
c, 36, 38, 44a, 44b, 44c
Rising portions 25a, 25b, 25c, 37 near
c, 39c, 45a, 45b, and 45c are substantially
According to this configuration, the water stop area generated in the downstream of the heat transfer tube 13 can be reduced, and the effective heat transfer area can be increased. The fin efficiency is high because the distance to the rise of the cut and raised is short, and each cut and raised 24a, 24b,
Since the sum of the lengths of 24c, 36, 38, 44a, 44b, and 44c is long, a larger portion of the temperature boundary layer leading edge effect can be secured more, and the heat transfer performance can be increased.

(17) Cutting and raising 24c, 36, 38,
The rising portion 25 of the side 44c which is not near the heat transfer tube 13
d, 37d, 39d, and 45d are formed in a direction substantially along the main flow direction A of the air flowing between the fins. According to this configuration, the air flow rectification effect is provided, and the ventilation resistance is not increased so much. Noise rise can be reduced.

[0087]

As is apparent from the above description, the heat exchanger with fins according to the first embodiment of the present invention has the following advantages.
By making one pass near the outlet in the pass, the supercooled liquid refrigerant cooled by the air is changed from two passes to one pass, thereby reducing the flow passage area of the refrigerant. For this reason, the refrigerant is accelerated, the heat transfer coefficient is greatly improved, the subcooling region that hardly contributes to heat exchange at the same degree of subcooling decreases, and as a result, the gas-liquid two-phase region that contributes to heat exchange increases. And the heat exchange capacity can be greatly improved.

(2) By providing the one-pass portion upstream with respect to the air inflow direction, the portion that has been cooled down due to supercooling during the condensation operation is arranged upstream with respect to the air inflow direction. In the case where the path is configured in a counter-current flow, the temperature gradient of the refrigerant is increased and the effect is increased,
Heat exchange capacity is improved.

(3) By providing two heat transfer tubes, which are the inlets of the refrigerant heat exchangers in the condensing operation, on the downstream side in the air inflow direction, the superheated refrigerant having the highest temperature in the condensing operation can be removed from the air. If the path is arranged in a counter-current direction with respect to the inflow direction of the refrigerant, the temperature gradient of the refrigerant is increased, the effect is increased, and the heat exchange capacity is improved.

(4) At the time of the condensation operation, two heat transfer tubes serving as inlets of the heat exchanger of the refrigerant are provided on the downstream side with respect to the inflow direction of the air, and one outlet portion is provided adjacent to the inlet portion and on the upstream side thereof. By providing the highest temperature and the lowest temperature of the refrigerant adjacent to each other, when the path is configured to be counter-current, the temperature gradient of the refrigerant increases and the effect increases, and the heat exchange capacity increases. Is improved.

(5) The fin is divided into two or more in the vertical direction, and the heat transfer tube at the final outlet of the one-pass portion of the outlet is provided at the end of the split portion of the fin so that the highest temperature inside the heat exchanger can be obtained. By dividing the fin into a lower outlet pipe and a high-temperature heat transfer pipe adjacent in the stepwise direction, the heat exchange due to heat conduction of both heat transfer pipes is prevented, thereby reducing loss inside the heat exchanger. This greatly improves the heat exchange capacity.

On the other hand, in the heat exchanger with fins according to the second to sixth embodiments of the present invention, the following effects can be obtained as is apparent from the above description. First, a plurality of main cut-and-raised portions are provided on one side of the surface of the fin between the heat transfer tubes adjacent to each other in the stepwise direction, and the width of the cut-and-raised portions in the column direction is set to approximately one of the distance between the adjacent cut-and-raised portions in the column direction. ３ to 、, the fins are divided at least at one position between the stages, and the heat transfer tubes communicate with each other to allow the refrigerant to pass therethrough. When used as a condenser, the total number of heat transfer tubes is 5 % Of the heat transfer tubes including the final outlet of the refrigerant having a percentage of 30% to 30%, the number of the refrigerant channels is 1; the number of the refrigerant channels of the other heat transfer tubes is 2.
The heat transfer tubes near the outlet including the final outlet of the refrigerant having the refrigerant flow path number of 1 are arranged in the most upwind row of the air, and the heat transfer tubes at the final outlet of the refrigerant are arranged at any of the fins at the inter-stage division points. The two heat transfer tubes at the inlet of the refrigerant are arranged at the end stages, and the two heat transfer tubes at the inlet and downstream of the heat transfer tubes near the outlet including the final outlet of the refrigerant having the number of refrigerant flow paths of one are the most downstream. Insulation means are provided on the fin surface near the center between the heat transfer tubes and the heat transfer tubes adjacent to the heat transfer tubes arranged in the row in the leeward direction, at least in the state of supercooled liquid or superheated gas. According to this configuration, the number of refrigerant passages in the heat transfer tube through which the refrigerant in the supercooled liquid state flows is set to 1, so that the condensing temperature is lowered and the degree of subcooling is increased. The heat transfer coefficient can be greatly improved without significantly increasing the refrigerant flow resistance. The heat exchange by heat conduction through the fins from the heat transfer tube at the final outlet of the refrigerant arranged at the end of the division point to the heat transfer tube adjacent in the step direction can be halved, and the inside of the supercooled liquid state The number of refrigerant flow paths through which the refrigerant flows is 1
The heat transfer tubes are arranged at the most upwind side, and the two heat transfer tubes at the refrigerant inlet through which the refrigerant in the superheated gas state flows are arranged in the most downstream row of the leeward or downstream stage. The heat exchange capacity can be improved by the effective effect, and heat insulation means provided in the fin portion near the central portion between the heat transfer tubes adjacent in the row direction allows fins between the refrigerant flowing inside each heat transfer tube to be finned. Heat conduction through the base can be suppressed, and the heat exchange capacity in a plurality of rows can be improved.

Further, as heat insulating means provided at least on the surface of the fin near the center between the heat transfer tube and the heat transfer tube adjacent to the heat transfer tube in the row direction, the heat transfer tube passing through at least the refrigerant in a supercooled liquid or superheated gas state. According to this configuration, it is possible to suppress heat conduction through the fin base between the refrigerant flowing inside the heat transfer tubes adjacent to each other in the row direction, and to perform cutting. The heat transfer performance can be improved by the temperature boundary layer leading edge effect of the portion.

Further, the length of the cut portion in the step direction is set to be not less than the diameter of the heat transfer tube and not more than about six times the step pitch. According to this configuration, the inside of the heat transfer tube adjacent in the row direction is formed. Heat conduction through the fin base between the flowing refrigerants can be effectively suppressed.

According to the configuration in which the end of the cut portion is provided near the end of one of the inter-stage division points of the fin in which the heat transfer tube of the final outlet of the refrigerant is disposed, the final outlet of the refrigerant having the lowest temperature is provided. Since the cut portion always exists between the heat transfer tube and the heat transfer tube adjacent to the heat transfer tube in the row direction, heat conduction through the fin base can be suppressed most effectively.

According to the structure in which a plurality of cut portions are continuously formed in the stepwise direction via the non-cut portions, the heat transfer performance can be further improved by the temperature boundary layer leading edge effect of the cut portions.

According to the configuration in which the cut portions are continuously connected in the stepwise direction via the non-cut portions, the heat transfer performance can be further improved by the temperature boundary layer leading edge effect of the cut portions.

[0098] The length of the non-cut portion is set to about 1 of the diameter of the heat transfer tube.
According to the configuration of / 2 or less, heat is conducted between the refrigerant flowing inside the heat transfer tubes adjacent to each other in the row direction through the non-cut portions, and it is possible to suppress a decrease in heat exchange capacity.

The length of the cut portion in the step direction and the length of the non-cut portion are mainly constant, and the total length of the finned heat exchanger in the step direction is determined by the length of the cut portion in the step direction and the length of the non-cut portion. When a remainder is generated that is not divisible by an integer when divided by the sum of, according to the configuration in which the length in the step direction of one cut portion is increased by a length corresponding to the remainder, cutting of a fixed length is performed. When processing fins by repeatedly using the mold of the part, it is possible to eliminate the non-cut part and form a cut part longer than the other part by shifting the fin only one place in the step direction by the length equivalent to the remainder and hitting twice. In addition, it is possible to easily obtain a finned heat exchanger in which the cutting section is continuously connected in all stages in the step direction through the non-cutting section.

According to the configuration in which the cut portion having a longer stepwise length is provided downwind of the air near the heat transfer tube near the outlet including the final outlet of the refrigerant having one refrigerant flow path, It is possible to effectively insulate the heat transfer tubes in which the coolant in the coolant state flows inside and the heat transfer tubes adjacent in the row direction.

According to the configuration in which the fins are divided into rows as the heat insulating means over the entire length in the step direction, it is possible to suppress the heat conduction through the fin base between the refrigerant flowing inside the heat transfer tubes adjacent in the row direction. In addition, the heat transfer performance can be improved by the temperature boundary layer leading edge effect.

According to a configuration in which cutouts having the same width as the plurality of main cutouts are provided on the same side as the surface on which the main cutouts are cutout as heat insulating means, heat transfer tubes adjacent in the row direction are provided. In addition to suppressing the heat transfer through the fin base between the refrigerant flowing inside the fin base, the heat transfer performance can be improved by the temperature boundary layer leading edge effect of the cut and raised, and all the cut and raised can be on the same side The maintenance of the mold is easy.

According to the structure in which the cut-and-raised portion having the same width as the main cut-and-raised portions is provided on the side opposite to the surface on which the cut-and-lead portions are raised, the heat transfer tubes adjacent in the row direction are provided. Between the refrigerant flowing inside the fin base, it is possible to suppress the heat conduction, and the heat transfer performance can be improved by the cut-and-raised temperature boundary layer leading edge effect. Can be obtained by easily remodeling one in which the front and back are alternately provided.

As a heat insulating means, a cut-and-raised portion having the same width as the main and plural cut-and-raised portions is provided on the side opposite to the main and multiple cut-and-raised portions. In the middle between, on the side opposite to the side where the main cuts are cut,
That is, according to the configuration in which a plurality of cut-and-raised portions having the same width as the main plurality of cut-and-raised portions are provided alternately, heat conduction through the fin base is suppressed between the refrigerant flowing inside the heat transfer tubes adjacent in the row direction. The heat transfer performance can be improved by the temperature boundary layer leading edge effect of the plurality of cut-and-raised portions provided alternately on the front and back sides.

The height of the cut-and-raised portion is set to approximately 1 / fin of the fin pitch.
According to the configuration of 2 to 2/3, the velocity distribution of the air between the fins is uniform, and the rise in ventilation resistance can be reduced.

The number of cut-and-raised portions is determined by n in order from the closest to the straight line connecting the centers of the heat transfer tubes adjacent in the step direction.
, N1, n2, n3,..., N1 ≦ n2 ≦ n3
≤ ... According to this configuration,
Local velocity distribution on the leeward side is less likely to occur, and the rise of blowing noise can be reduced.

According to the configuration in which the cut-and-raised rising portion near the heat transfer tube is formed substantially in the direction and position along the outer periphery of the heat transfer tube, the water stoppage area generated downstream of the heat transfer tube is reduced, and the effective heat transfer area is reduced. The fin efficiency is high because the distance from the heat transfer tube to the rise of the cut-out is short, and the sum of the lengths of each cut-out is long, so it is possible to secure a larger portion of the temperature boundary layer leading edge effect. , Heat transfer performance can be increased.

According to the structure in which the rising portion of the cut and raised portion on the side other than the vicinity of the heat transfer tube is formed in a manner substantially along the main flow direction of the air flowing between the fins, it has a rectifying effect of the air flow and does not significantly increase the ventilation resistance. In addition, it is possible to reduce an increase in blowing noise.

[Brief description of the drawings]

FIG. 1 is a configuration diagram of a finned heat exchanger according to a first embodiment of the present invention.

FIG. 2 is a plan view of fins of a finned heat exchanger according to a second embodiment of the present invention.

FIG. 3 is a plan view of fins of a finned heat exchanger according to a third embodiment of the present invention.

FIG. 4 is a plan view of a fin of a finned heat exchanger according to fourth and fifth embodiments of the present invention.

5A is a detailed plan view of a fin of a finned heat exchanger according to a fourth embodiment of the present invention, and FIG. 5B is a cross-sectional view taken along line VB-VB in FIG. 5A. is there.

6A is a detailed plan view of a fin of a finned heat exchanger according to a fifth embodiment of the present invention, and FIG. 6B is a cross-sectional view taken along line VIB-VIB in FIG. 6A. is there.

FIG. 7 is a plan view of fins of a finned heat exchanger according to a sixth embodiment of the present invention.

8A is a detailed plan view of a fin of a finned heat exchanger according to a sixth embodiment of the present invention, and FIG. 8B is a cross-sectional view taken along line VIIIB-VIIIB in FIG. 8A. is there.

9A is a plan view showing a configuration of a fin common to the finned heat exchangers according to the second to sixth embodiments of the present invention, and FIG. 9B is a plan view showing IXB- in FIG. 9A. It is a layer sectional view in the IXB line.

FIG. 10 is a front view showing a configuration of a refrigerant passage common to the finned heat exchangers according to the second to sixth embodiments of the present invention.

FIG. 11 is a configuration diagram of a conventional finned heat exchanger.

FIG. 12A is a first conventional example of Japanese Patent Application Laid-Open No. 63-18 / 1988.
It is a top view of the fin of the heat exchanger with a fin of 3391 publication, (B) is sectional drawing which follows the XIIB-XIIB line of FIG.12 (A).

FIG. 13A shows a second conventional example of Japanese Patent Laid-Open No. 2-217.
FIG. 13 is a plan view of the fins of the finned heat exchanger disclosed in Japanese Patent Publication No. 792, and FIG. 13B is a cross-sectional view taken along line XIIIB-XIIIB of FIG.

[Explanation of symbols]

Reference Signs List A A main flow direction of air B Inter-stage division of fins 1 Inlet pipe 2 Inlet pipe 6 Outlet pipe 11 Fin 12 Fin color 13 Heat transfer pipe 17a, 18a Heat transfer pipe at refrigerant inlet 19a, 19b, 19c Heat transfer pipe near refrigerant outlet 19d Heat transfer tube 24a, 24b, 24c at final outlet of refrigerant Main cut-and-raised 25a, 25b, 25c Stand-up portion near cut-and-raised heat transfer tube 25d Start-up portion not cut and raised near heat transfer tube 31 Cut portion 32 Not cut Part 33 Cutting part with increased length in stepwise direction 34 End of cutting part 35 Splitting part between rows 36 Cut-and-raised 37c Stand-up part near cut-and-raised heat transfer tube 37d Stand-up part near cut-and-raised side of heat transfer tube 38 Cut-and-raised 39c Stand-up portion near the cut-and-raised heat transfer tube 39d Cut-and-raised heat transfer tube Rising portions 44a, 44b, and 44c on non-near-side side 45a, 45b, 45c Rising portions near side of cut-and-raised heat transfer tube 45d Rising portions on side not near the heat-transfer tube when cut and raised

Claims (23)

[Claims] A plurality of elongated fins arranged in parallel with each other at regular intervals, between which air flows in a predetermined direction;
In the finned heat exchanger, which has a plurality of heat transfer tubes that are inserted into the fins at right angles in a plurality of rows while the refrigerant passes through the inside, during the condensation operation, the heat transfer tubes have two passages at the refrigerant inlet and two outlets. A heat exchanger with fins, wherein 5 to 30% of all heat transfer tubes are in one pass in the vicinity. 2. The heat transfer tube row is substantially separated from each other in the predetermined direction, and the heat transfer tube of one pass is provided upstream of the heat transfer tube row in the predetermined direction. Item 2. A finned heat exchanger according to Item 1. 3. A row of heat transfer tubes which are generally separated from each other in the predetermined direction and serve as an inlet for a heat exchanger of the refrigerant.
The finned heat exchanger according to claim 1, wherein the heat transfer tubes are provided downstream of the row of heat transfer tubes in the predetermined direction. 4. A row of heat transfer tubes which are substantially separated from each other in the predetermined direction and serve as an inlet for a heat exchanger of a refrigerant.
The heat transfer tubes are provided in the predetermined direction such that the heat transfer tubes of one path near the outlet are adjacent to the heat transfer tubes at the entrance while the heat transfer tubes are provided downstream of the row of heat transfer tubes in the predetermined direction. The finned heat exchanger according to claim 1, wherein the heat exchanger is provided upstream of the fin. 5. The fin is divided into at least two fin portions in a transverse direction at a split point, and further, the last heat transfer tube of the heat transfer tube in one pass near the outlet is connected to the fin near the split point. The finned heat exchanger according to claim 1, wherein the heat exchanger is provided with a fin. 6. A heat-insulating means on a surface of a fin near at least a central portion between a heat-transfer tube and a heat-transfer tube laterally adjacent to the fin, wherein the heat-transfer tube passes through at least a refrigerant in a supercooled liquid or superheated gas state. The finned heat exchanger according to any one of claims 2 to 4, further comprising: 7. A plurality of cut-and-raised portions on one side of the surface of the fin between the heat transfer tubes adjacent in the longitudinal direction of the fin, and further, the width of the cut-and-raised portion of the fin is reduced by the lateral cut-and-raised portion of the fin. The finned heat exchanger according to claim 6, wherein the distance is set to approximately 1/3 to 1/2 of the interval. 8. The finned heat exchanger according to claim 6, wherein the heat insulating means is formed by a cut portion extending in a longitudinal direction of the fin. 9. The finned heat exchanger according to claim 8, wherein the length of the cut portion in the longitudinal direction of the fin is not less than the diameter of the heat transfer tube and not more than about six times the interval between the heat transfer tubes in the longitudinal direction of the fin. . 10. The fin is divided laterally at a split location into at least two fin sections, and further, the last one of the heat transfer pipes in the one-pass section near the outlet is connected to the vicinity of the fin split location. 9. The finned heat exchanger according to claim 8, wherein an end of the cut portion is provided near a division of a fin portion where the final heat transfer tube is provided. 11. The heat exchanger with fins according to claim 8, wherein a plurality of cut portions are continuously formed in a stepwise direction via a non-cut portion. 12. The finned heat exchanger according to claim 8, wherein the cutting section is continuous in all steps in the step direction via the non-cutting section. 13. The length of the non-cut portion is set to about 1 of the diameter of the heat transfer tube.
The finned heat exchanger according to claim 11 or 12, wherein the heat exchanger is not more than / 2. 14. The stepwise length of the cutting portion and the length of the non-cutting portion are respectively mainly constant, and the total length of the finned heat exchanger in the stepwise direction is set to the stepwise length of the cutting portion and the non-cutting portion. The fin with the fin according to claim 12, wherein, when divided by the sum of the lengths, if the remainder is not divisible by an integer, the stepwise length of one cut portion is increased by a length corresponding to the remainder. Heat exchanger. 15. The method according to claim 14, wherein the cut portion having a longer stepwise length is provided on the downwind side of the air near the heat transfer tube near the outlet including the final outlet of the refrigerant having one refrigerant flow path. Heat exchanger with fins as described. 16. The heat exchanger with fins according to claim 6, wherein the fins are divided in rows in the stepwise direction over the entire length as the heat insulating means. 17. The finned heat exchanger according to claim 7, wherein another cut-and-raised portion having the same width as the cut-and-raised portion is provided on the same side as the cut-and-raised surface as the heat insulating means. 18. The finned heat exchanger according to claim 7, wherein another cut-and-raised portion having the same width as the cut-and-raised portion is provided on the side opposite to the cut-and-raised portion as the heat insulating means. 19. As a heat insulating means, a plurality of other cut-and-raised portions having the same width as the cut-and-raised portion are provided on the side opposite to the surface on which the cut-and-raised portion is cut, and a center between the cut-and-raised portions in the row direction is provided. 8. The finned heat exchanger according to claim 7, wherein a cut-and-raised portion and a separate cut-and-raised portion are provided on the side opposite to the cut-and-raised surface. 20. The finned heat exchanger according to claim 7, wherein the height of the cut-and-raised portion is approximately 1/2 to approximately 2/3 of the fin pitch. 21. Assuming that the number of cut-and-raised portions is n1, n2, n3,... In ascending order from a straight line connecting the centers of heat transfer tubes adjacent in the step direction, n1 ≦ n2 ≦
7. The method according to claim 7, wherein n3.ltoreq.
10. The finned heat exchanger according to any one of 9 above. 22. The heat exchanger with fins according to claim 7, wherein the rising portion of the cut-and-raised portion near the heat transfer tube is formed substantially in the direction and position along the outer periphery of the heat transfer tube. 23. The finned heat exchanger according to claim 7, wherein the rising portion of the cut-and-raised portion on the side other than the vicinity of the heat transfer tube is formed by a method substantially along the predetermined direction.