KR100740180B1 - Finned heat exchanger and method of manufacturing the same - Google Patents

Abstract

In the heat exchanger with fins, the front side heat exchanger 20 and the rear side heat exchanger 40 are each provided with a plurality of fins 21 and 41 arranged in parallel at predetermined intervals, and are inserted at right angles to these fins. It is comprised by the many heat exchanger tube 11 in which a refrigerant flows inside. The fin in the front side heat exchanger connects two straight portions and their two straight portions, each of which the upstream leading edges 22 and 23 and the downstream trailing edges 32 and 33 each have the same obtuse angle. It is formed by a curved portion 24, 34 to be bent, and close to the perfusion blower 5 of the two regions sandwiched by a straight upstream leading edge and a straight downstream trailing edge of the pin. The distance B between the upstream leading edge and the downstream trailing edge in the region on the side is shorter than the distance A between the upstream leading edge and the downstream trailing edge in the region on the side far from the perfusion blower. It is.

Description

Finned heat exchanger and its manufacturing method {FINNED HEAT EXCHANGER AND METHOD OF MANUFACTURING THE SAME}

The present invention relates to a heat exchanger with a fin and a method of manufacturing the same.

Generally, as shown in FIG. 5, the indoor unit of an air conditioner has one or more suction ports, such as the inlet port 62a of the front surface and the inlet port 62b of the upper surface, and the blower outlet 63 of the lower surface as shown in FIG. One or more ejection openings are formed, and the heat exchanger 64 with the perfusion blower 65 and the fin is housed in the case body 61.

This conventional finned heat exchanger 64 is disposed on the front surface side in the case body 61, and is provided with a main front side heat exchanger 64A and a case body (bended in the vicinity of the center portion in the vertical direction). It consists of the back side heat exchanger 64B arrange | positioned at the back side in 61, and the auxiliary heat exchangers 64C and 64D which were respectively attached to the front side of the front side heat exchanger 64A. The front side heat exchanger 64A and the rear side heat exchanger 64B are arranged in such a manner as to surround the perfusion blower 65 from the upstream side to accommodate the heat exchanger with a fin as large as possible in a limited space. . In addition, although auxiliary heat exchangers 64C and 64D are provided in order to improve the heat exchange capacity, after manufacturing in a process different from the main front side heat exchanger 64A and back side heat exchanger 64B, Since it is additionally connected to the front side heat exchanger 64A and the back side heat exchanger 64B, FIG. 5 shows the case where it is further connected to the main front side heat exchanger 64A. In the vicinity of the bent portion of the front side heat exchanger 64A, if only the front side heat exchanger 64A is bent and a space without fins is generated, the airflow may pass through the heat exchanger with fins almost without heat exchange. In order to prevent such a problem, the spacer 66 is arrange | positioned.

On the other hand, the bending process of 64 A of front side heat exchangers is unnecessary, and it removes this spacer 66, and prevents airflow from passing through a heat exchanger with a fin, without heat exchange, and is made of a Japanese patent. In the specification concerning 3091830, the structure which formed the front side heat exchanger in circular arc shape is disclosed.

In this patent document, as shown in FIGS. 6A, 6B, and 7, the shape of the fin 72 of the front side heat exchanger 71A is formed in an arc shape so as to surround a part of the circumferential surface of the perfusion blower 73. An indoor unit of an air conditioner is disclosed. The heat exchanger pipe 74 inserted into this front side heat exchanger 71A at substantially right angles is provided in multiple rows, and the upstream and downstream heat | fever of these heat exchanger tubes 74 is provided. Are arranged to draw isosceles triangles from each other. Therefore, as a result, the step pitch A of the downstream heat-transfer pipe 74 arrange | positioned inside the arc-shaped part is the step pitch of the heat transfer pipe 74 of the upstream row arrange | positioned outside the arc-shaped part. It is formed smaller than (B).

According to this structure, since the spacer 66 becomes unnecessary and waste material does not generate | occur | produce in the location corresponding to the spacer 66 in the material of the pin 72 at the time of manufacture, the waste material of the material of the pin 72 is reduced. In addition, there is an advantage that only three types of bending pitches of the hairpins and the return bands for communicating the heat transfer tubes 74 with each other are A, B, and C. In addition, since the spacer 66 is not provided, the area of the fin 72 increases by the portion corresponding to the spacer 66, and the heat exchange capacity is improved.

However, in the heat exchanger with fins described in the patent specification, since the front side heat exchanger 71A is arcuate and the slope of the upper portion of the fin 72 becomes smooth, a heat exchanger with fins is used as the evaporator. In this case, water condensed on the upper portion of the fins 72 stays, or in the worst case, the condensate does not flow along the fins 72, and the water droplets fall to the perfusion blower 73, resulting in water droplets from the jet port 75. This may be scattered.

The present invention solves this conventional problem, improves the shape of the finned heat exchanger and its manufacturing method, and attaches the fins as large as possible to the limited space of the indoor unit of the air conditioner, especially the narrow space. The purpose of the present invention is to provide a heat exchanger with fins that accommodates heat exchangers, and allows for a significant improvement in heat exchange capacity, and allows the water condensed on the fin surface to flow smoothly along the fins when used as an evaporator. It is.

Moreover, it aims at obtaining the manufacturing method of the heat exchanger with a fin which can manufacture cheaply the heat exchanger with a fin.

In order to solve the above problems, the heat exchanger with a fin according to the present invention comprises a case body having a suction port at the front side and a blower outlet at the lower side thereof, and a wind circuit configured as a perfusion blower accommodated in the case body. As mounted in the indoor unit of the air conditioner,

 A front side heat exchanger and a rear side heat exchanger disposed in the middle of the wind circuit from the inlet to the perfusion blower or in the middle of the wind circuit from the perfusion blower to the blower outlet,

The front side heat exchanger and the back side heat exchanger are each composed of a plurality of fins arranged in parallel at predetermined intervals and a gas flow therebetween, and a plurality of heat transfer tubes inserted at right angles to the fins and having a refrigerant flowing therein. Become,

The fin in the front side heat exchanger is formed between two straight portions and two straight lines whose upstream leading leading edge and downstream side trailing edge each have the same obtuse angle. While being formed in a bent shape by one curved portion connecting the

The distance between the upstream leading edge and the downstream trailing edge in the region near the perfusion blower among the two regions fitted with the straight upstream leading edge and the straight downstream trailing edge of the pin formed in a bent shape. Is shorter than the distance between the upstream leading edge and the downstream trailing edge in the region far from the perfusion blower.

According to this configuration, the upstream leading edge and the downstream trailing edge of the fin in the front side heat exchanger are each formed of two straight portions having the same obtuse angle and one curved portion connecting the two straight lines. Upstream side in the area | region near the perfusion blower among two area | regions formed in the shape and fitted by the linear upstream leading edge of a fin in a bent front heat exchanger, and the linear downstream trailing edge. Since the distance between the leading edge and the downstream trailing edge is shorter than the distance between the upstream leading edge and the downstream trailing edge in the region far from the perfusion blower, it is more confined to a limited space, especially a narrow space. The heat exchanger with a large fin is housed, and a greater heat exchange capacity is exhibited. In addition, the front side heat exchanger does not need to be bent later, and of course, the spacer which is needed when bending is not necessary. In the case where the finned heat exchanger is used as the evaporator, the water droplets condensed on the fins in the front side heat exchanger and the rear side heat exchanger respectively move on the continuous fins and flow smoothly. In addition, since the upper side of the fin in the front side heat exchanger is inclined at a constant angle close to the vertical surrounded by the straight line of the upstream leading edge and the straight line of the downstream trailing edge, water droplets condensed on the surface of the fin during evaporation There is no stay.

Further, in the heat exchanger, the distance between the upstream leading edge and the downstream trailing edge in the region near the perfusion blower is 20 to 23 mm, and the upstream side in the region far from the perfusion blower. The distance between the leading edge and the downstream trailing edge is 24 to 27 mm.

According to this configuration, the upstream reading in the region far from the perfusion blower among the two regions fitted by the straight upstream leading edge of the fin and the straight downstream trailing edge of the fin in the bent front heat exchanger. While the distance between the edge and the downstream trailing edge is thin at 24 to 27 mm, the distance between the upstream leading edge and the downstream trailing edge in the region near the perfusion blower is even thinner at 20 to 23 mm. As a result, the depth width required for the wind circuit including the heat exchanger can be significantly reduced, thereby making the indoor unit thin.

Further, both curved portions on the upstream leading edge side and the downstream trailing edge side of the fin in the heat exchanger have the same shape.

According to this configuration, the curved portion of each of the upstream leading edge and the downstream trailing edge of the fin of the front side heat exchanger has the same shape, so that the waste material of the fin does not come out much when the fin is continuously pressed. Therefore, it can produce efficiently.

Moreover, the curved part of the fin of the front side heat exchanger in the said heat exchanger is circular arc shape.

According to this configuration, the curved portions of each of the upstream leading edge and the downstream trailing edge of the fin in the front side heat exchanger are arc-shaped, which facilitates the processing and maintenance of the press die of the fin.

Further, in the heat exchanger, the upstream leading edge and the downstream trailing edge of the fin in the back side heat exchanger are constituted by straight lines parallel to each other, and the distance between the upstream leading edge and the downstream trailing edge of the fin. (A) Upstream leading edge and downstream trailing in the region far from the perfusion blower among the two regions fitted by the linear upstream leading edge of the fin and the linear downstream trailing edge of the fin in the front side heat exchanger. It is equal to the distance of the edge.

According to this configuration, by configuring the upstream leading edge and the downstream trailing edge of the rear side heat exchanger in parallel straight lines, the heat exchanger with the larger fins can be accommodated in a limited space, thereby exhibiting a greater heat exchange capacity. have. In addition, about the fin, it can be set as one fin in the state in which the upper end part of the fin in a front side heat exchanger and the upper end part of the fin in a back side heat exchanger are connected, and in this case, it can be continuous press work with high productivity. .

Further, in the heat exchanger, a heat transfer tube inserted into the fin portion of the region far from the perfusion blower among the two regions fitted by the linear upstream leading edge of the fin and the linear downstream trailing edge of the fin in the front side heat exchanger; The outer diameter of the heat exchanger tube inserted into the straight portion of the upstream leading edge of the fin and the straight portion of the downstream trailing edge of the rear side heat exchanger is 4 to 6.4 mm, and in the thermal direction along the mainstream direction of the gas. The heat transfer tubes are arranged in three rows, and the arrangement pitch of the heat transfer tubes in the short direction perpendicular to the mainstream direction of the base is 14.5 to 16 mm.

According to this configuration, of the two regions sandwiched by the linear upstream leading edge of the fin and the linear downstream trailing edge of the fin in the front side heat exchanger, the region far from the perfusion blower and the upstream side of the rear side heat exchanger The heat pipes having an outer diameter of 4 to 6.4 mm are arranged in three rows and the unidirectional pitch is 14.5 to 16 mm for the area fitted between the straight portion of the edge and the straight portion of the downstream trailing edge, and the unidirectional pitch is 14.5 to 16 mm. The heat transfer rate on the air side can be obtained, and therefore, the air volume at the same noise can be improved to exhibit high heat exchange capacity.

Further, in the heat exchanger, a heat transfer tube inserted into the fin portion of the region far from the perfusion blower among the two regions fitted by the linear upstream leading edge of the fin and the linear downstream trailing edge of the fin in the front side heat exchanger; The heat exchanger tube inserted into the linear part of the upstream leading edge of the fin in the back side heat exchanger, and the part inserted by the linear part of the downstream trailing edge is comprised by the heat exchanger tube of two types of outer diameters,

In addition, the heat exchanger tube of larger outer diameter is arrange | positioned at the most upstream column of gas flow, and the refrigerant | coolant when the heat exchanger with a fin is used as a condenser or a gas cooler as a heat exchanger tube near a refrigerant | coolant outlet, or as an evaporator. Heat transfer tube near the inlet, formed by one pass,

In the case of a heat pipe having a smaller outer diameter, when the heat exchanger with fins is used as a condenser or a gas cooler, when a heat exchanger with a coolant upstream or as an evaporator is used as an evaporator than the heat pipe having a larger outer diameter, The heat transfer pipe on the downstream side of the refrigerant rather than the heat transfer pipe of the outer diameter is formed by four passes, and the refrigerant flows respectively.

According to this structure, the heat exchanger tube of the outer diameter of the refrigerant | coolant inlet vicinity when the said heat exchanger with a fin is used as a condenser or a gas cooler or a refrigerant | coolant inlet vicinity of the refrigerant | coolant inlet vicinity when an evaporator is used as a gas of a three-row structure is used. By arranging in one pass by arranging in the most upstream heat of the flow, the heat transfer rate in the pipe can be improved and the heat exchange capacity can be increased since the arrangement is opposed to the temperature difference between the air and the refrigerant. In addition, since the refrigerant in this region has a high density, it does not increase the refrigerant flow resistance so much, and therefore does not prevent the increase in the heat exchange capacity. In the range of the outer diameter of 4 to 6.4 mm, the outer diameter of the one smaller than the heat transfer tube near the refrigerant inlet when the heat exchanger with the fin is used as the condenser or the gas cooler as the heat transfer tube near the refrigerant outlet or the evaporator is used. When the heat transfer tube is used as a heat transfer tube upstream of the refrigerant rather than the heat transfer tube formed in one pass near the refrigerant outlet when the heat exchanger with fins is used as a condenser or a gas cooler, or when the heat exchanger with fins is used as an evaporator. By forming four passes as the heat transfer tubes downstream of the refrigerant rather than the heat transfer tubes formed in one pass near the inlet, the heat exchange capacity can be increased by making both the high heat transfer rate in the tube and the low refrigerant flow resistance.

Further, in the heat exchanger, a heat transfer tube inserted into the fin portion of the region near the perfusion blower among the two regions fitted by the linear upstream leading edge of the fin and the linear downstream trailing edge of the fin in the front side heat exchanger, and The outer diameter of the heat exchanger tube inserted into the portion of the region sandwiched by the curved upstream leading edge and the curved downstream trailing edge of the fin is in the range of 6.5 to 8.5 mm, respectively, and becomes the direction along the mainstream direction of the gas. The heat transfer tubes are arranged in two rows in the column direction, and the arrangement pitch of the heat transfer tubes in the unidirectional direction perpendicular to the mainstream direction of the base is 16 to 22 mm.

According to this configuration, of the two regions sandwiched by the linear upstream leading edge of the fin and the linear downstream trailing edge of the fin in the front side heat exchanger, the region near the perfusion blower and the curved side of the front side heat exchanger In the region fitted between the upstream leading edge and the curved downstream trailing edge, two rows of heat transfer tubes having an outer diameter of 6.5 to 8.5 mm and a unidirectional pitch of 16 to 22 mm were used in the two-row configuration. Although the airflow resistance is slightly higher, the high air-side heat transfer rate can be obtained, and the airflow distribution can be improved by reducing the difference in the airflow resistance of the heat exchanger as a whole. Thus, the air volume at the same noise can be improved to achieve excellent performance. have.

Further, in the heat exchanger, the arrangement pitch in one direction of the heat transfer tube inserted into the portion of the region sandwiched between the curved upstream leading edge of the fin and the curved downstream trailing edge of the fin in the front side heat exchanger, The column on the upstream side of the flow is equal to or less than the column on the downstream side.

According to this structure, the number of unidirectional directions of the heat exchanger tube inserted into the part of the area | region which is inserted by the curved upstream leading edge of the fin and the curved downstream trailing edge in the front side heat exchanger is made as large as possible, and this area | region Since the ventilation resistance of is increased, the wind speed distribution of the finned heat exchanger can be made more uniform, and therefore, a greater heat exchange capacity can be exhibited.

Further, in the heat exchanger, the fin portion of the region near the perfusion blower and the curved shape of the fin among the two regions sandwiched by the linear upstream leading edge of the fin and the linear downstream trailing edge of the fin in the front side heat exchanger. The heat exchanger tubes respectively inserted in the portion of the region fitted by the upstream leading edge and the trailing trailing edge of the shape consist of two outer diameters,

In addition, the said heat exchanger tube of the larger outer diameter is arrange | positioned in the most downstream row of gas flow, and the refrigerant | coolant at the time of using the heat exchanger with a fin as a condenser or a gas cooler as a heat exchanger tube near a refrigerant | coolant inlet, or an evaporator. It is used as a heat pipe near the exit,

When the heat exchanger with a fin is used as a condenser or a gas cooler, when the heat exchanger with a smaller outer diameter is used as a condenser or a gas cooler, the larger one is used as a heat exchanger downstream of a refrigerant | coolant downstream, or as an evaporator than the said heat exchanger with a larger outer diameter. The heat transfer tubes on the upstream side of the refrigerant rather than the heat transfer tubes of the outer diameter are formed in two passes, respectively, and the refrigerant flows.

According to this structure, the outer diameter of the heat exchanger tube near a refrigerant | coolant inlet when a heat exchanger with a fin is used as a condenser or a gas cooler, or the heat exchanger tube near a refrigerant | coolant outlet when using it as an evaporator is compared with any other heat exchanger tube in the range of 6.5-8.5 mm. In addition to being thickened and arranged in two passes in a row downstream of the flow of gas in a two-row configuration, the performance improvement by counterflow arrangement with respect to the temperature difference between air and refrigerant is obtained, and the heat transfer rate in the pipe is Although slightly lowered, the refrigerant flow resistance can be greatly reduced, and thus the heat exchange capacity can be significantly increased. In addition, in the range whose outer diameter is 6.5-8.5 mm, the heat exchanger tube of the outer diameter smaller than the heat exchanger tube near the refrigerant | coolant outlet when the heat exchanger with a fin is used as a condenser or a gas cooler, or a heat exchanger tube near a refrigerant | coolant outlet when it is used as an evaporator. In the case where the finned heat exchanger is used as a condenser or gas cooler, the heat exchanger tube on the downstream side of the coolant is formed as a heat exchanger downstream of the refrigerant rather than the heat transfer tube formed in two passes of the largest outer diameter near the refrigerant outlet, or the heat exchanger with fins is used as the evaporator. When used, the heat transfer tube on the upstream side of the refrigerant is formed in two passes as the heat transfer tube on the upstream side of the refrigerant rather than the heat transfer tube formed in two passes of the largest outer diameter near the refrigerant outlet, whereby the heat transfer rate in the tube can be improved to increase the heat exchange capacity.

Yet, in the heat exchanger, the shortest distance between the heat transfer tube and the upstream leading edge or the downstream trailing edge of the fin is 1.8 mm or more.

According to this configuration, the distance between the heat transfer tube and the upstream leading edge or the downstream trailing edge of the fin is set to be 1.8 mm at the shortest. Therefore, when the heat exchanger with the fin is used as an evaporator, it flows on the surface of the fin. The falling condensed water contacts the heat transfer pipe, thereby suppressing the phenomenon of splashing from the upstream leading edge or the downstream trailing edge of the fin.

In the heat exchanger, when the dehumidification operation is performed by dividing the reheater and the evaporator in one direction, the two heat exchangers are fitted with a straight upstream leading edge of the fin and a straight downstream trailing edge of the fin in the front heat exchanger. In the region, the region far from the perfusion blower and the rear side heat exchanger are used as reheaters,

In the front side heat exchanger, of the two regions fitted with the straight upstream leading edge of the fin and the straight downstream trailing edge, the region near the perfusion blower and the upstream leading edge of the fin and the curved The region sandwiched by the downstream trailing edge is used as the evaporator.

According to this configuration, good dehumidification operation can be performed by properly balancing the heat loads of the reheater and the evaporator. In addition, since the reheater is disposed above the vertical direction of the evaporator, the condensed water condensed on the fins in the region of the evaporator can be prevented from reaching the surface of the fins of the reheater and re-evaporating to humidify the room.

Further, in the heat exchanger, a plurality of cutoff portions are formed on the fin surface between the heat transfer tubes adjacent in the unidirectional direction to open in the mainstream direction of the gas,

The raised portion near each heat transfer tube of each cut portion is formed in the direction along the circumference of the heat transfer tube, and the ratio of the width between the cut portions adjacent in the column direction to the width of the heat direction of the cut portions is 2 to 2.5. have.

According to this configuration, a high air-side heat transfer rate is obtained by the temperature boundary layer leading edge effect of a plurality of cutout portions formed by opening in the mainstream direction of the gas on the fin surface between adjacent heat transfer tubes in one direction, and at the same time. Since the raised portion near the heat transfer tube in the raised portion is formed in the direction along the circumference of the heat transfer tube, the air flow can be led to the wake portion of the heat transfer tube, thus increasing the effective heat transfer area, thereby improving heat exchange performance. By setting the ratio of the widths of the cutting portions adjacent to each other in the column direction to the width in the column direction (pin substrate) to 2 to 2.5, the heat exchange capacity can be improved compared to the case where the conventional ratio is approximately 3. have.

Moreover, in the said heat exchanger, the height of a cutting part is set to 1/4-3/4 of the pitch of adjacent fins.

According to this configuration, by setting the height of the cutout portions to 1/4 to 3/4 of the pitches of the adjacent pins, the air volume at the same noise can be increased and a greater heat exchange capacity can be exhibited.

In the heat exchanger, the height of the cut-out portion is 1/2 of the pitch between adjacent fins for the region having a large wind speed in which the heat exchanger with the fin approaches the perfusion blower, and the other region. And 3/4 of the pitch of adjacent pins.

According to this structure, in the area | region where the wind speed which the said heat exchanger with a fin approaches to a perfusion blower is large, the height of a cut-out part is made into 1/2 of the pitch of adjacent fins, and makes a ventilation resistance relatively large, In other areas, the airflow resistance of the finned heat exchanger can be made more uniform by reducing the ventilation resistance to 3/4 of the pitch of adjacent fins, thereby providing greater heat exchange capacity. Can be.

In the heat exchanger, the shortest distance between the cutout portion and the upstream leading edge or the downstream trailing edge of the fin is 1.8 mm or more.

According to this configuration, the distance between the cutout portion and the upstream leading edge or the downstream trailing edge of the fin is set to be 1.8 mm as the shortest, so that when the heat exchanger with the fin is used as the evaporator, it is attached to the surface of the fin. The condensed water which flows down along a cut-out part can suppress the phenomenon which bounces off from the upstream leading edge or the downstream trailing edge of a fin.

In the heat exchanger, when there is a temperature difference between the refrigerant flowing through the two heat transfer tubes adjacent to each other in the column direction, the notch portion is formed in the direction along the one direction on the fin of the central portion between the rows of the two heat transfer tubes.

According to this configuration, when there is a temperature difference between two heat transfer tubes adjacent to each other in the column direction, the notch is formed in the direction along the unidirectional direction to the pins in the central portion between the rows of the two heat transfer tubes. Since the heat exchange loss due to heat conduction passing through the fin can be prevented, the heat exchange capacity is not lowered.

In the heat exchanger, when the dehumidification operation is performed by dividing the reheater and the evaporator in one direction, the notch portion is formed while leaving the uncut portion in the fin portion between the reheater region and the evaporator region.

According to this configuration, when dehumidification operation is performed by using the heat exchanger with fins in one direction divided into a reheater and an evaporator, a not cut portion is left in the fin between the region of the reheater and the region of the evaporator. By forming it, the fall of the heat exchange ability drastically by the heat conduction of a fin can be prevented. When the entire finned heat exchanger is used as an evaporator, the water condensed on the surface of the fin can flow smoothly through the connected portion of the fin without retaining water in the notch.

In the heat exchanger, any one of HFC refrigerant, HC refrigerant, and carbon dioxide is used as the refrigerant flowing in the heat transfer tube.

According to this structure, by using any one of HFC refrigerant | coolant, HC refrigerant | coolant, and carbon dioxide with a small ozone destruction coefficient as a refrigerant fluid which flows inside a heat exchanger tube, it can contribute to protection of a global environment. In particular, since HC refrigerant and carbon dioxide are refrigerants having a small global warming coefficient, they can contribute to the protection of the global environment.

In the heat exchanger, since the upper end of the fin of the front side heat exchanger and the upper end of the fin of the rear side heat exchanger are manufactured,

For a unidirectional direction perpendicular to the mainstream direction of the gas of a fin color for inserting a heat transfer tube formed in the fin in a state where the upper end of the fin in the front side heat exchanger and the upper end of the fin in the rear side heat exchanger are connected. About the pitch

The arrangement pitch of the fin color of the location adjacent to the boundary part of the said front side heat exchanger and the said back side heat exchanger is shorter than the arrangement pitch in another unidirectional direction.

According to this structure, the waste material of a fin material can be reduced compared with the case where the unidirectional pitch of the fin color of the location adjacent to the boundary part of a front side heat exchanger and a back side heat exchanger is equal to the pitch of the unidirectional vicinity of another vicinity. have.

The manufacturing method of the heat exchanger of this invention is a manufacturing method of the said heat exchanger provided with a front side heat exchanger and a back side heat exchanger,

After laminating a plurality of fins obtained by successively pressing the fins in the state in which the upper end of the fin in the front side heat exchanger and the upper end of the fin in the back side heat exchanger are connected at the boundary portion, a plurality of fins are laminated. Let's

Next, each of the fins is cut at the boundary between the front side heat exchanger and the back side heat exchanger and separated into the front side heat exchanger and the back side heat exchanger.

According to this manufacturing method, compared with the case of separately manufacturing the front side heat exchanger and the back side heat exchanger, the heat exchanger with fins can be manufactured efficiently. Moreover, the thing of which the diameter of the heat exchanger tube inserted into one fin, the number of rows, the heat pitch, or the stage pitch differs can be mixed, or the one fin can mix the shape and height of a cutting part.

In the method of manufacturing the heat exchanger, when the upper end of the fin of the front side heat exchanger and the upper end of the fin of the rear side heat exchanger are successively press-worked as one fin in a state of being connected at a boundary,

After stacking a plurality of fins formed with shorter pitches than the other unidirectional pitches for the unidirectionally adjacent portions of the fin color for inserting the heat transfer tubes into the front side heat exchanger and the rear side heat exchanger, respectively, Insert the heat pipe through the pin color,

Next, the fin is separated into the front side heat exchanger and the back side heat exchanger.

According to this manufacturing method, it is possible to reduce the waste of the fin material as compared with the case where the unidirectional pitch of the fin color at the adjacent position at the boundary between the front side heat exchanger and the back side heat exchanger is equal to the pitch of the unidirectional direction in the vicinity. Can be.

BRIEF DESCRIPTION OF THE DRAWINGS It is sectional drawing of the indoor unit of the air conditioner which accommodated the finned heat exchanger which concerns on embodiment of this invention.

2 is a side view of the fin of the heat exchanger having the same fin.

3 is an enlarged side view of the main portion of the fin of the heat exchanger having the same fin.

It is a side view which shows the image which arranged the fin of the heat exchanger with the same fin continuously in the feed direction of two presses.

5 is a cross-sectional view of an indoor unit of an air conditioner containing a conventional finned heat exchanger.

6A is a schematic side view of a fin of another conventional finned heat exchanger, and FIG. 6B is a schematic cross-sectional view of an indoor unit of an air conditioner accommodating a finned heat exchanger using fins shown in FIG. 6A.

It is a figure which shows the relationship of the arrangement | positioning pitch of the heat exchanger tube in the fin of the other conventional heat exchanger with fin.

EMBODIMENT OF THE INVENTION Hereinafter, the heat exchanger with a fin which concerns on embodiment of this invention, and its manufacturing method are demonstrated, referring drawings. The results of the study shown in the following examples and the accompanying drawings illustrate the present invention without limiting the scope of the invention defined in the claims.

First, the indoor unit of the air conditioner in which the finned heat exchanger which concerns on this embodiment is mounted is demonstrated based on FIG. 1 is a longitudinal cross-sectional view of this indoor unit.

As shown in FIG. 1, inlet bodies 3a and 3b are formed on the front face and the upper face of the case body 2 of the indoor unit 1 of this air conditioner, and a blower outlet 4 is formed on the lower face thereof. In the case body 2, the through-flow blower 5 and the heat exchanger 10 with fins are accommodated.

The finned heat exchanger 10 includes a front side heat exchanger 20 disposed on the front side inside the case body 2 and a back side heat exchanger 40 disposed on the back side inside the case body 2. The front side heat exchanger 20 and the back side heat exchanger 40 are arranged so as to surround the perfusion blower 5 from the upstream side.

Each of the heat exchangers 20 and 40 is arranged in parallel at predetermined intervals, and a plurality of fins 21 and 41 in which air flows therebetween, and are inserted at right angles to these fins 21 and 41 so as to be inside. The heat exchanger tube 11 has a plurality of heat transfer tubes 11 through which a refrigerant (refrigerant fluid) flows, and the fins 21 and 41 are separated from each other in the front heat exchanger 20 and the rear heat exchanger 40. By communicating with (11), it acts as one heat exchanger.

Next, the heat exchanger with a fin which concerns on embodiment, and its manufacturing method are demonstrated using FIG. 1 and FIGS.

2 is a side view of the fin 21 of the front side heat exchanger 20 and the fin 41 of the rear side heat exchanger 40 of the finned heat exchanger according to the embodiment, and FIG. 3 is a front side heat exchanger thereof. It is an enlarged side view of the main part of the pin 21 of 20. Fig. 4 is a view of one sheet in which the upper ends of the fins 21 of the front side heat exchanger 20 and the fins 41 of the rear side heat exchanger 40 of the finned heat exchanger of Fig. 2 are connected at the boundary. It is a side view which shows the image which arranged two pins which can be press-processed continuously as the pin 13 in the feed direction of a press.

As shown in FIG. 2 and FIG. 3, each of the upstream leading edge portion and the downstream trailing edge portion of the fin 21 of the front side heat exchanger 20 has the angles θ1 and θ2 of the intersection portions of the extension lines. ) And two straight portions 22, 23 and 32, 33 each having the same obtuse angle, and one curved portion 24, 34 connecting the two straight portions 22, 23 and 32, 33, respectively. It is formed in the shape of "ku" consisting of), ie, in a bent shape. Here, the linear portions 22 and 32 and 23 and 33 are parallel to each other. Moreover, although the shape as the curved part 24 and 34 has an elliptic curve, a hyperbola, a spline, etc., the curved part 24 of an upstream leading edge part, and the curved part 34 of a downstream trailing edge part have the same dimension. It is shaped. In addition, in this embodiment, as shown to FIGS. 1-4, the curved part 24 of the upstream leading edge part, and the curved part 34 of the downstream trailing edge part become circular arc shape, and they are the same curvature. It is formed with a radius. Moreover, the upstream leading edge part and the downstream trailing edge part of the fin 41 of the back side heat exchanger 40 are comprised by the parallel straight part 42 and 43. As shown in FIG.

Of the two regions fitted to the straight upstream leading edge of the fin 21 of the bent front heat exchanger 20 and the straight downstream trailing edge, one of the regions near the perfusion blower 5 The distance between the upstream leading edge and the downstream trailing edge, i.e., the distance B between the upstream leading edge 23 and the downstream trailing edge 33, is the area on the other side far from the perfusion blower 5. Is formed shorter than the distance A between the upstream leading edge and the downstream trailing edge, i.e., the distance A between the upstream leading edge 22 and the downstream trailing edge 32. Moreover, one area | region has shown the upper part rather than the bent part of the heat exchanger 20 formed in the bending shape, and the other area | region has shown the lower part than the bent part of the heat exchanger 20 formed in the bending shape.

In the heat exchanger with a fin according to the present embodiment, the distance A between the parallel straight upstream leading edge 22 and the downstream trailing edge 32 (one side), which is recommended in view of heat transfer performance and ventilation resistance (one side) (Area area | region) is 24-27 mm and the distance B (the other area | region) of the parallel upstream leading edge 23 and downstream trailing edge 33 is 20-23 mm.

2 and 4, the distance between the upstream leading edge 42 and the downstream trailing edge 43 of the fin 41 of the back side heat exchanger 40 is a front side heat exchanger having a bent shape. Upstream leading edge 22 of one area | region far from perfusion blower 5 among two areas | intervals fitted by the linear upstream leading edge and the linear downstream trailing edge of fin 21 of machine 20. ) Is equal to the distance A of the downstream trailing edge 32.

As shown in FIG. 4, the fin 21 of the front side heat exchanger 20 and the fin 41 of the back side heat exchanger 40 are as one fin 13 in which the upper end part was connected in the boundary part. It is manufactured by continuous press working. Further, the angle at which the straight upstream leading edge 22 or the downstream trailing edge 32 on the straight side away from the through-flow blower 5 of the fin 21 of the front side heat exchanger 20 forms the feed direction of the fin. ?, The angle at which the straight upstream leading edge 23 or the downstream trailing edge 33 on the side close to the through-flow blower 5 forms the feed direction of the pin press is β, and the pin is fed at the time of the pin press. If the width is set to C, the relations of α + β = θ1 = θ2 and A / sinα = B / sinβ = C are established. Therefore, α, β, and C are unique from the known θ1 = θ2, A, and B. Is determined.

In addition, as shown in FIG. 4, when the fin 13 (21, 41) is continuously press-formed and manufactured from a metal plate, the both ends and the front surface of the fin 13 (21, 41) are due to the circumstances of storage of the heat exchanger 10 with fins. In the part between the side heat exchanger 20 and the back side heat exchanger 40, the part which cuts off will generate | occur | produce, but since the waste materials 51, 52, 53 which generate | occur | produce at that time are a little, others are used without waste and continuously The pin 13 is manufactured.

As shown in FIG. 3, the pin color 12 is burring | drilled by the round hole shape in each pin 13. As shown in FIG.

As shown in FIG. 4, the fin 13 manufactured by continuously press-processing as one fin with the fin 21 of the front side heat exchanger 20 and the fin 41 of the back side heat exchanger 40 connected is manufactured. ), A plurality of heat transfer pipes (11) are inserted (inserted through) through the fin collars (12), and then the heat transfer tubes (11) are enlarged in order to closely contact the fin collars (12) and the heat transfer tubes (11). The fin 13 is cut at the boundary between the front side heat exchanger 20 and the rear side heat exchanger 40, and is separated into the front side heat exchanger 20 and the rear side heat exchanger 40.

As shown to FIG. 1 and FIG. 2, it becomes a direction orthogonal to the diameter of the heat exchanger tube 11 and the mainstream direction (flow direction) of the gas (air) in the heat exchanger tube 11, so-called unidirectional pitch and For the so-called row number, that is, row number, along the mainstream direction, two fitted into a straight upstream leading edge and a straight downstream trailing edge of the fin 21 of the bent front heat exchanger 20. Out of the two regions, the region on the side farther from the through-flow blower 5, the straight upstream leading edge 42 of the fin 41 of the back side heat exchanger 40 and the straight downstream trailing edge 43. In the sandwiched region, they are formed differently.

That is, of the two regions sandwiched by the straight upstream leading edge of the fin 21 of the bent front heat exchanger 20 and the straight downstream trailing edge, the region farther from the flow blower 5, In other words, the region interposed between the straight upstream leading edge 22 and the straight downstream trailing edge 32 and the straight upstream leading edge 42 of the fin 41 of the back side heat exchanger 40 As the heat exchanger tube 11 inserted into the fins 21 and 41 of the area | region fitted by the downstream trailing edge 43, the big heat exchanger tube 11a of the outer diameter of the range of 4-6.4mm, and the small heat exchanger tube The heat exchanger tubes of two types of outer diameters of (11b) are used (consisted), arranged in three rows in the column direction, and formed as 14.5 to 16 mm with respect to the pitch D in the unidirectional direction. In addition, of the two regions sandwiched by the straight upstream leading edge of the fin 21 of the bent front heat exchanger 20 and the straight downstream trailing edge, the region near the perfusion blower 5, That is, the region fitted by the linear upstream leading edge 23 and the linear downstream trailing edge 33 and the curved upstream leading edge 24 and the curved downstream in the front side heat exchanger 20. As the heat exchanger tube 11 inserted into the fin 21 of the area | region fitted by the side trailing edge 34, the small heat exchanger tube 11c of the outer diameter of the range of 6.5-8.5 mm, and the big heat exchanger tube 11d of Two types of heat transfer tubes of outer diameter are used (consisted), arranged in two rows in the column direction, and formed as 16 to 22 mm with respect to the pitch E in the unidirectional direction.

In addition, as shown in FIG. 3, the heat exchanger tube 11c inserted into the fin 21 of the area | region which is fitted by the curved upstream leading edge and the curved downstream trailing edge in the front side heat exchanger 20, For the unidirectional pitch E of 11d), the heat pitch Eu on the upstream side of the flow of gas is equal to or less (same or smaller) than the heat pitch Ed on the downstream side of the flow of gas. Formed.

In addition, although the flow of the refrigerant | coolant at the time of using the heat exchanger 10 with fins which concerns on this embodiment as an evaporator is shown in FIG. 1, the straight line of the fin 21 of the front-side heat exchanger 20 of a bent shape is shown. Of the two regions sandwiched by the upstream leading edge and the linear downstream trailing edge, the region far from the perfusion blower 5, that is, the straight upstream leading edge 22 and the linear downstream trailing edge 32. ) And the fins 21 and 41 in the region fitted by the linear upstream leading edge 42 and the linear downstream trailing edge 43 of the fin 41 of the back side heat exchanger 40. Refrigerant inlet at the time of placing six heat exchanger tubes 11a of large outer diameter in the outermost upstream column of gas flow among the two types of heat exchanger tubes 11 of the outer diameter of 4-6.4mm inserted. It is used (formed) in one pass as heat transfer pipe of the neighborhood, and of small outer diameter Exchanger heat transfer pipe (11b) for, by using a 4-pass than the heat transfer tube (11a) of the larger outer diameter of a heat transfer pipe of the refrigerant downstream side (formed), the refrigerant is flowing.

Thereafter, the coolant passes through the dehumidification throttle means 80 in a fully open state except at the time of dehumidification operation, and the straight upstream leading edge of the fin 21 of the bent front heat exchanger 20 Of the two regions fitted by the straight downstream trailing edge, the region near the perfusion blower 5, that is, the region fitted by the linear upstream leading edge 23 and the linear downstream trailing edge 33, And 6.5 to 8.5 mm inserted into the fin (fin portion) 21 in the region fitted by the curved upstream leading edge 24 and the curved downstream trailing edge 34 of the front side heat exchanger 20. Of the two types of heat transfer tubes 11 having the outer diameter, the heat transfer tube 11c having the smaller outer diameter flows in two passes (two paths), and finally, the coolant has an outer diameter near the coolant outlet when the coolant is used as an evaporator. Four large heat transfer pipes (11d) flow in two passes and flow out from the heat exchanger with fins. All. Moreover, the four heat exchanger tubes 11d of the larger outer diameter near the refrigerant | coolant outlet when using as an evaporator are arrange | positioned at the most downstream row of gas flow.

In addition, although the heat pipe 11 uses four types of outer diameters, when it speaks with the outer diameter before expansion, the heat pipe 11a is 6 mm, the heat pipe 11b is 5 mm, the heat pipe 11c is 7 mm, and the heat pipe 11d is used. Is recommended to use 8 mm.

By the way, based on FIG. 1, although the case where the finned heat exchanger 10 of this embodiment was used as an evaporator was demonstrated, when the finned heat exchanger of this embodiment is used as a condenser or a gas cooler, Although the flow direction of the refrigerant is reversed, other configurations are the same as those used as the evaporator.

In addition, when dehumidification operation is carried out by dividing the heat exchanger 10 with a fin of this embodiment into a reheater and an evaporator in one direction, the straight line of the fin 21 of the front side heat exchanger 20 of a bent shape. Of the two regions sandwiched by the upstream leading edge on the top and the downstream trailing edge on the straight line, the region on the side farther from the perfusion blower 5, that is, the upstream leading edge 22 on the straight line and the downstream trailing edge on the straight line ( 32 and the straight upstream leading edge of the fin 21 of the bent front heat exchanger 20 and the straight downstream trailing edge using the region fitted in the 32 and the back side heat exchanger 40 as reheaters. Among the two regions fitted with the front side, the front side heat exchanger 20 and the region sandwiched by the straight upstream leading edge 23 and the straight downstream trailing edge 33 on the side near the perfusion blower 5. Curved upstream leading edge 24 with It utilizes the area between the downstream side trailing edge (34) as an evaporator. In this dehumidification operation, as shown in FIG. 1, the refrigerant flows into the evaporator from the reheater via the throttle means 80 in which an appropriate throttle amount is set.

In addition, as shown in FIG. 4, the fin 21 of the front side heat exchanger 20 and the fin 41 of the back side heat exchanger 40 are connected to the fin 1 of the state in which these upper ends were connected by the boundary part. 13), when produced by continuous press working, the arrangement pitch of the portion where the fin color 12 of each of the front side heat exchanger 20 and the rear side heat exchanger 40 is adjacent in a unidirectional direction is different. The pitch F is shorter than the pitch D in the unidirectional direction.

As shown in Fig. 2 and Fig. 3, a plurality of cutout portions opened in the mainstream direction of the gas are formed at positions between the heat transfer tubes 11 adjacent to each other in the unidirectional direction in the fins 13 (21, 41). 141, 151, 161, 142, 152 are formed, and the raised portions 141a, 151, 161, 142, 152 of the cut portions 141, 151, 161, 142, 152 are formed at a location near the fin color 12, that is, at a location near the heat transfer pipe 11. , 142a and 152a are formed in the direction along the circumference of the heat exchanger tube 11.

Here, as shown in FIG. 3, the width | variety (adjacent in a column direction) with respect to the width | variety Ws1 of each cut | disconnecting part 141, 151, 161 in the column direction, and the pin part between cut | disconnecting parts 141, 151, 161 adjoining in a column direction. Cutting portions 142 and 152 adjacent in the column direction with respect to the ratio Wb1 / Ws1 of the width of the plate portion of the fin 21 to Wb1 and the width Ws2 in the column direction of the cutting portions 142 and 152. The ratio Wb2 / Ws2 of the width | variety of the fin part of the liver (width of the flat part of the fins 21 and 41 adjacent to a column direction) Wb2 is set to 2-2.5.

The heights of the cutout portions 141, 151, 161, 142 and 152 along the thickness direction of the pins 21 and 41 are set to 1/4 to 3/4 of the pitch of the adjacent pins 13 (21 and 41).

In addition, in order to obtain high heat exchange performance, the heights of the cutting portions 141, 151, 161 are adjacent to a region G having a high wind speed by approaching the perfusion blower 5 in a region having a high wind speed, for example, in FIG. It is set to 1/2 of the pitch of the pins 13 (21, 41) to be described, and 3/4 of the pitch of the adjacent pins 13 (21, 41) to the other areas.

3, the upstream leading edges 22, 23, 24, 42 or the downstream trailing edges 32, 33 of the heat transfer pipes 11a, 11b, 11c, 11d and the fins 21, 41. Shortest distance Lt of 34,43, and upstream leading edges 22, 23, 24, 42 or downstream trailing edges 32, 33 of cutouts 141, 151, 161, 142, 152 and pins 21, 41 The shortest distance Ls of (34,43) is set to 1.8 mm or more.

In addition, as shown in FIG.2 and FIG.3, when there exists a temperature difference between the refrigerant | coolants which flow inside, between two heat exchanger tubes 11 which adjoin in a column direction, these two heat exchanger tubes 11 (pin color 12 The notch part 17 is formed in the pin part of the center part between the rows of ()) in the direction along a unidirectional direction.

In the case where the air conditioner is dehumidified and the heat exchanger 10 with fins of the indoor unit 1 is divided into a reheater and an evaporator in one direction, the front side heat exchanger 20 shown in FIG. Although the lower portion is used as the evaporator from the curved portions 24 and 34 of the fin 21 and the other portion is used as the reheater, the area of the reheater and the evaporator in the fin 21 in this case are used. The notch part 19 is formed in the part between area | regions, leaving the part 18 which was not cut | disconnected.

As the refrigerant flowing (flowing) inside the heat transfer pipe 11 of the heat exchanger 10 with fins, any one of HFC refrigerant, HC refrigerant, and carbon dioxide is used.

As described above, the fins 21 and 41 of the front side heat exchanger 20 and the rear side heat exchanger 40 are continuously press-processed as one fin 13 in a state where the upper ends are connected at the boundary portions, respectively. And a plurality of fins 13 are stacked, and then the heat transfer tube 11 is inserted (inserted through) into the fin collar 12 so as to expand, and the front side heat exchanger 20 and the rear side heat exchanger ( 40 is manufactured with the fins 13 (21, 41) connected, and then the front side heat exchanger 20 and the back side heat exchanger 40 are cut at the boundary between the fins 21, 41. Thus, manufacturing is performed by separating the front side heat exchanger 20 and the back side heat exchanger 40.

As described above, the upstream leading edge and the downstream trailing edge of the fin 21 of the front side heat exchanger 20 connect two straight portions each having the same obtuse angle and between these two straight lines. Perfusion blower among two regions formed in a bent shape consisting of one curved portion and fitted into a straight upstream leading edge and a straight downstream trailing edge of the fin 21 of the bent front heat exchanger 20. The distance between the upstream leading edge 23 and the downstream trailing edge 33 of one region near the side 5 is determined by the upstream leading edge of the other region on the side farther from the perfusion blower 5 ( By shorter than the distance between 22) and the downstream trailing edge 32, a larger fin-attached heat exchanger 10 can be accommodated in a limited space, especially a narrow space, whereby a greater heat exchange capacity can be exhibited. In addition, the front side heat exchanger 20 does not need to be bent later, and of course, the spacers required when bending are not necessary. In addition, when using the heat exchanger 10 with fins as an evaporator, the water droplets condensed on the fins 21 and 41 of the front side heat exchanger 20 and the rear side heat exchanger 40 are each successive fins. Roll (21,41) to run smoothly. In addition, since the upper side of the fin 21 of the front side heat exchanger 20 is inclined at a constant angle close to the vertical surrounded by the straight line of the upstream leading edge 22 and the straight line of the downstream trailing edge 32, The water droplets condensed on the surface of the fins do not stay at the time.

In addition, of the two regions sandwiched by the straight upstream leading edge and the straight downstream trailing edge of the fin 21 of the bent front heat exchanger 20, The distance between the upstream leading edge 22 and the downstream trailing edge 32 is 24 to 27 mm, and at the same time, the upstream leading edge 23 and the downstream trail in the region near the perfusion blower 5 are provided. Since the distance of the ring edge 33 is 20-23 mm which is thinner than that, the depth width required for the wind circuit containing a heat exchanger becomes quite small, and the indoor unit 1 can be made thin.

Moreover, the fin 13 is continuously press-formed by making the curved part 24 and 34 of the upstream leading edge and the downstream trailing edge of the fin 21 of the front side heat exchanger 20 the same shape. In doing so, it is possible to efficiently produce the waste materials 51, 52, and 53 of the pin 13 without generating much.

Further, the curved portions 24 and 25 of the upstream leading edges and the downstream trailing edges of the fins 21 of the front side heat exchanger 20 are arc-shaped, thereby forming a press die of the fins 13. Machining and maintenance are easy.

Moreover, by making the upstream leading edge 42 and the downstream trailing edge 43 of the back side heat exchanger 40 into a parallel straight line, the heat exchanger 10 with larger fins is accommodated in a limited space. Thus, greater heat exchange capacity can be exhibited.

In addition, the fin 13 of the heat exchanger 10 with fins measures the distance between the upstream leading edge 42 and the downstream trailing edge 43 of the fin 41 of the rear side heat exchanger 40. , Upstream of the region on the side farther from the through-flow blower 5 of the two regions fitted by the straight upstream leading edge of the fin 21 of the bent front heat exchanger 20 and the straight downstream trailing edge. Since the distance between the side leading edge 23 and the downstream trailing edge 33 is equal, the upper end of the fin 21 of the front side heat exchanger 20 and the upper end of the fin 41 of the rear side heat exchanger 41 Can be used as one pin in a connected state, and therefore, continuous press working can be performed with high productivity.

In addition, of the two regions sandwiched by the straight upstream leading edge of the fin 21 of the front side heat exchanger 20 and the straight downstream trailing edge, the region on the side farther from the perfusion blower 5, that is, the upstream side. An area fitted between the leading edge 22 and the downstream trailing edge 32 and a straight portion of the upstream leading edge 42 of the rear side heat exchanger 40 and a straight portion of the downstream trailing edge 43. In the area, by arranging three rows of heat transfer pipes 11a and 11b having an outer diameter of 4 to 6.4 mm and setting the pitch of 14.5 to 16 mm, the air-side heat transfer is not increased. In addition to being able to obtain a rate, it is possible to increase the amount of air flow at the same noise and to exhibit a high heat exchange capacity.

Moreover, the heat exchanger tube 11 in which the finned heat exchanger 10 is used as a condenser or gas cooler, or the heat exchanger tube 11 near a refrigerant | coolant inlet when it is used as an evaporator, ranges from 4 to 6.4 mm. Among the heat transfer tubes 11a and 11b having the outer diameter of, the heat transfer tube 11a having the larger outer diameter is arranged in the most upstream column of the flow of gas in a three-row configuration and used (formed) in one pass. The heat transfer rate can be improved, and the heat exchange capacity can be increased since the arrangement can be made counterflow with respect to the temperature difference between the air and the refrigerant. In addition, since the refrigerant in this region has a high density, the refrigerant flow resistance does not increase so much and does not prevent the increase in heat exchange capacity. In addition, in the range of 4 to 6.4 mm in outer diameter, the heat transfer tube 11a near the refrigerant outlet when the heat exchanger 10 with fins is used as a condenser or gas cooler, or the heat transfer tube near the refrigerant inlet when the evaporator is used. Refrigerant upstream than the heat exchanger tube 11a which uses the heat exchanger tube 11b of the outer diameter smaller than 11a) as one pass near a refrigerant | coolant outlet when the heat exchanger 10 with the said fin is used as a condenser or a gas cooler. In the case of using the heat transfer tube on the side or the heat exchanger with fins as the evaporator, it is used (formed) as a heat transfer tube on the downstream side of the refrigerant rather than the heat transfer tube 11a used in one pass near the refrigerant inlet. Therefore, the heat exchange capacity can be increased by achieving a high pipe heat transfer rate and a low refrigerant flow resistance.

In addition, of the two regions sandwiched by the straight upstream leading edge of the fin 21 and the straight downstream trailing edge of the fin 21 in the front side heat exchanger 20, the region near the perfusion blower 5, that is, the upstream. The area fitted between the side leading edge 23 and the downstream trailing edge 33 and the curved upstream leading edge 24 and the curved downstream trailing edge 34 of the front side heat exchanger 20. In the sandwiched area, the heat transfer pipes 11c and 11d having an outer diameter of 6.5 to 85 mm are arranged in two rows, and the unidirectional pitch is 16 to 22 mm. Since a high air-side heat transfer rate can be obtained, and the wind speed distribution can be improved by reducing the difference in the ventilation resistance of the entire heat exchanger, it is possible to improve the air volume at the same noise and to exhibit excellent heat exchange ability.

Moreover, the heat exchanger tube 11 inserted in the part of the area | region inserted by the curved upstream leading edge 24 and the curved downstream trailing edge 34 of the fin 21 in the front side heat exchanger 20 is shown. For the unidirectional pitch of), since the column on the upstream side of the gas flow is equal to or less than the heat on the downstream side of the gas flow, the number of heat transfer pipes 11 in the unidirectional direction is increased as much as possible in this region. Since the ventilation resistance can be increased, and thus the wind speed distribution of the heat exchanger 10 with fins can be made more uniform, a greater heat exchange capacity can be exhibited.

In addition, the outer diameter of the heat exchanger tube 11d near the refrigerant inlet when the heat exchanger 10 with fins is used as a condenser or gas cooler or the heat transfer tube 11d near the refrigerant outlet when the evaporator is used is 6.5 to 8.5 mm. In the range and thicker than any other heat pipes 11a, 11b, and 11c, and arranged in a row downstream of the flow of gas in a two-row configuration, the two passes are used (formed). While the performance improvement by the countercurrent arrangement is obtained, the heat transfer rate in the tube slightly decreases, but the refrigerant flow resistance can be greatly reduced, and thus the heat exchange capacity can be greatly increased. In addition, in the range of 6.5-8.5 mm in outer diameter, the heat exchanger tube 11d near a refrigerant | coolant inlet when the heat exchanger 10 with a fin was used as a condenser or a gas cooler, or the heat exchanger tube near a refrigerant | coolant outlet when used as an evaporator ( 11d) is used in two passes of the largest outer diameter in the vicinity of the refrigerant outlet when the heat exchanger tube 11c having the smaller outer diameter is used as the condenser or the gas cooler. 11d heat transfer tube 11d used as a heat transfer tube downstream of the refrigerant, or in the case where the finned heat exchanger 10 is used as an evaporator, the heat transfer tube 11d used in two passes of the largest outer diameter in the vicinity of the refrigerant outlet By using two passes as the heat transfer tube on the upstream side of the refrigerant, the heat transfer rate in the tube can be improved to increase the heat exchange capacity.

Further, the distance between the heat pipes 11a, 11b, 11c, 11d and the upstream leading edges 22, 23, 24, 42 or the downstream trailing edges 32, 33, 34, 43 of the fins 21, 41. Since the heat exchanger 10 with fins is used as the evaporator, the condensed water flowing down and attached to the surfaces of the fins 21 and 41 is transferred to the heat transfer tubes 11a, 11b, 11c, and 11d. It is possible to suppress the phenomenon of jumping from the upstream leading edges 22, 23, 24, 42 or the downstream trailing edges 32, 33, 34, 43 of the pins 21, 41.

When the dehumidification operation is performed by dividing the heat exchanger 10 with fins into a reheater and an evaporator in one direction, the straight upstream side of the fin 21 in the bent front side heat exchanger 20. Backside heat exchange and the area on the side farther from the perfusion blower 5, the area fitted to the upstream leading edge 22 and the downstream trailing edge 32, between the leading edge and the straight downstream trailing edge. Perforation among two regions fitted with a straight upstream leading edge and a straight downstream trailing edge of the fin 21 in the bent front face heat exchanger 20 using the machine 40 as a reheater. Curved upstream side of fin 21 in front side heat exchanger 20 and region sandwiched by upstream leading edge 23 and downstream trailing edge 33 near the blower 5. Leading edge 24 and curved downstream trailing edge By using the area between the 34 as an evaporator, dehumidification operation can be performed in good to be properly balanced the thermal load of the reheater and the evaporator. In addition, since the reheater is disposed above the vertical direction of the evaporator, the condensed water condensed on the fins in the region of the evaporator can be prevented from reaching the surface of the fins of the reheater and re-evaporating to humidify the room.

Further, the temperature boundary layer leading edges of the cutouts 141, 151, 161, 142, and 152 formed by opening in the mainstream direction of the gas on the surfaces of the fins 21, 41 between the heat transfer tubes 11 adjacent to each other in one direction. By the effect, a high air side heat transfer rate is obtained, and the rising parts 141a, 151a, 161a, 142a, and 152a near the heat transfer pipe 11 of these cutouts 141, 151, 161, 142, and 152 are obtained. Since it is formed in the direction along the circumference of the heat exchanger tube 11, airflow can be guide | induced to the downstream part of the heat exchanger tube 11, and therefore an effective heat transfer area increases, and heat exchange performance can be improved. Further, the ratio Wb1 / Ws1 of the widths Wb1 and Wb2 between the cutting portions adjacent to each other in the column direction with respect to the widths Ws1 and Ws2 in the column direction of the cutting portions 141, 151, 161, 142, and 152. By setting Wb2 / Ws2 to 2 to 2.5, the heat exchange capacity can be improved compared to the case where the conventional ratio is approximately 3.

In addition, the height of each cut | disconnected part 141, 151, 161, 142, 152 was made into 1/4-3/4 of the pitch of adjacent pins 13 (21, 41), and the same noise The air volume of the city can be increased, and greater heat exchange ability can be obtained.

In addition, the heights of the cut portions 141, 151, 161, 142, and 152 are set to be adjacent to the fins 13 (21, 41) for the region G having a large wind speed where the heat exchanger 10 with fins approaches the perfusion blower 5. )] To make the ventilation resistance relatively large by ½ of the pitch of each other, and to 3/4 of the pitch of adjacent fins [13 (21,41)] for other areas, and to make the ventilation resistance smaller than that. As a result, the wind speed distribution of the heat exchanger 10 with fins can be made more uniform, and thus a greater heat exchange capacity can be exhibited.

Further, the shortest distances of the cutting portions 141, 151, 161, 142, 152 and the upstream leading edges 22, 23, 24, 42 or the downstream trailing edges 32, 33, 34, 43 of the pins 21, 41 are shortest. Since the heat exchanger 10 with a fin was used as an evaporator, the condensed water adhering to the surface of the fin 21, 41 flows along the cut-outs 141, 151, 161, 142, and 152, and the fin 21 Bounce off from the upstream leading edges 22, 23, 24, 42 or the downstream trailing edges 32, 33, 34, 43.

In addition, between two heat transfer pipes 11 adjacent to each other in the column direction, when there is a temperature difference in the fluid flowing inside, the direction along the one direction to the fins 21 and 41 in the center portion between the rows of the two heat transfer pipes 11. By forming the notch portion 17, the heat exchange loss due to the heat conduction passing through the fins 21 and 41 can be prevented, so that the heat exchange capacity is not lowered.

In addition, when dehumidification operation is performed by dividing the heat exchanger 10 with fins into the reheater and the evaporator in one direction, the portion not cut into the fins 21 and 41 between the region of the reheater and the region of the evaporator. By forming the notch portion 19 by leaving 18, it is possible to prevent a significant drop in the capacity due to the heat conduction of the fins 21 and 41. When the entire finned heat exchanger 10 is used as an evaporator, the fins 21 and 41 are connected without the water condensed on the surfaces of the fins 21 and 41 in the notches 19. The part 18 can flow smoothly.

In addition, by using any one of HFC refrigerant, HC refrigerant, and carbon dioxide having a small ozone depletion coefficient, the refrigerant fluid flowing inside the heat transfer pipe 11 can contribute to the protection of the global environment. In particular, since HC refrigerant and carbon dioxide are refrigerants having a small global warming coefficient, they can contribute to the protection of the global environment.

In addition, the upper end part of the fin 21 in the front side heat exchanger 20 and the upper end part of the fin 41 in the back side heat exchanger 40 are continuously press-processed as one fin 13 in the state connected. At the time, the pitch of the fin collar 12 for inserting the heat transfer tube 11 later in the direction perpendicular to the mainstream direction of the base is adjacent to each other at the boundary between the fins 21 and 41. Since the pitch F in the one-way direction of the fin color is made shorter than the pitch D in the other direction, the pitch of the fin color at the adjacent position at the boundary between the front side heat exchanger 20 and the rear side heat exchanger 40 ( As compared with the case where F) is equal to the pitch D in the other unidirectional direction, the waste material 52 of the fin material can be reduced.

In addition, the manufacturing method of the heat exchanger 10 with a fin includes the front side heat exchanger 20 arrange | positioned at the front side in the case body 2, and the back side arrange | positioned at the back side in the case body 2. A manufacturing method for manufacturing a finned heat exchanger (10) consisting of a side heat exchanger (40), the upper end of a fin (21) and a rear heat exchanger (40) of a front side heat exchanger (20). The upper end of the fin 41 is continuously press-processed as one fin 13 in a state where the upper end is connected at the boundary portion, and a plurality of fins 13 are stacked to insert and expand the heat pipe 11, and then the fin ( 13 is cut at the boundary between the front side heat exchanger 20 and the rear side heat exchanger 40 and separated into the front side heat exchanger 20 and the rear side heat exchanger 40, so that the front side heat exchanger 20 Compared to the case of separately manufacturing the heat exchanger 40 and the rear side heat exchanger 40, a finned heat exchanger 10 can be manufactured efficiently. Can be. In addition, the heat pipes 11a, 11b, 11c, and 11d of the heat transfer tubes 11a, 11b, 11c, and 11d inserted into the one fin 13 may have different diameters, different heat counts, different thermal pitches or unidirectional pitches, or one fin 13 The cutouts 141, 151, 161, 142, and 152 formed may be mixed in different shapes and heights.

Moreover, it is comprised so that the pitch F of the fin color 12 of the location adjacent to the boundary part of the front side heat exchanger 20 and the back side heat exchanger 40 may be shorter than the pitch D of another adjacent one direction. As for the manufacturing method of the heat exchanger 10 with a fin, the upper end part of the fin 21 in the front side heat exchanger 20 and the upper end part of the fin 41 in the back side heat exchanger 40 are described. The front side heat exchanger 20 is about the pitch of the fin 13 in the connected state which is laterally perpendicular to the mainstream direction of the gas of the fin collar 12 for inserting the heat transfer tube 11 later. And the pitch F of the pin color 12 adjacent to each other at the boundary of the back side heat exchanger 40 is formed shorter than the pitch D in the other unidirectional neighborhood, and a plurality of these fins 13 are stacked. The heat transfer tube 11 is inserted and expanded, and then the fin 13 is connected to the boundary between the front side heat exchanger 20 and the rear side heat exchanger 40. Since the front side heat exchanger 20 and the back side heat exchanger 40 are separated from each other, the fin color of a portion adjacent to the boundary between the front side heat exchanger 20 and the back side heat exchanger 40 ( The waste material 52 of fin material can be reduced compared with the case where the unidirectional pitch F of 12) is made equal to the pitch D of the unidirectional direction of another vicinity.

In addition, in the said embodiment, although the case where the suction ports 3a and 3b were formed in the front surface, the upper surface, etc. was demonstrated, it is not limited to this. In addition, although the case formed in the lower surface side was demonstrated as the jet port 4, it is not limited to this, The said structure is applicable also to what is formed in the front surface etc ..

In addition, in the said embodiment, although the case where the front side heat exchanger 20 and the back side heat exchanger 40 were arrange | positioned in the middle of the wind circuit from the intake port 3a, 3b to the perfusion blower 5 was demonstrated, It is not limited to this, For example, the said structure is applicable also to the heat exchanger arrange | positioned in the middle of the wind circuit from the flow-through blower 5 to the blower outlet 4. Moreover, it is applicable also to what is provided with three or more heat exchangers in an indoor unit, and only one is installed.

According to the heat exchanger with a fin according to the present embodiment, the shape of the finned heat exchanger composed of the front side heat exchanger and the rear side heat exchanger mounted in the indoor unit of the air conditioner and the manufacturing method thereof are improved. The upstream leading edge and the downstream trailing edge of the fin of the side heat exchanger are formed in a bent shape consisting of two straight portions each having the same obtuse angle and one curved portion connecting the two straight lines. Of the upstream leading edge and the downstream trailing edge of the region near the perfusion blower among the two regions fitted with the straight upstream leading edge of the fin and the straight downstream trailing edge of the fin in the front face heat exchanger. The distance is made shorter than the distance between the upstream leading edge and the downstream trailing edge of the region far from the perfusion blower, and the front side heat exchanger The curved portion of each of the upstream leading edge and the downstream trailing edge of the fin in the same shape has the same shape, and the upstream leading edge and the downstream trailing edge of the fin in the back side heat exchanger are constituted by parallel straight lines. The distance between the upstream leading edge and the downstream trailing edge of the fin in the side heat exchanger is fitted into the straight upstream leading edge and the straight downstream trailing edge of the fin in the bent front side heat exchanger. By making the distance equal to the distance between the upstream leading edge and the downstream trailing edge of the region far from the perfusion blower in the region, the indoor unit of the air conditioner is attached as large a pin as possible in a confined space, especially a narrow space. Water is condensed on the fin surface when the heat exchanger is accommodated, and the heat exchange capacity is greatly improved, and when used as an evaporator. It can be unloaded smoothly flowing along the pin. Moreover, according to the manufacturing method of the heat exchanger with fins, since it presses continuously as one fin which the fin in the front side heat exchanger and the fin in the back side heat exchanger connected, the waste material of a fin material does not come out efficiently and efficiently It can be manufactured at low cost.

As described above, the present invention relates to the improvement of the shape and dimensions of the fins in the heat exchanger and the improvement of the arrangement of the heat transfer tubes, and is particularly applicable to the indoor unit of the air conditioner, and between the refrigerant flowing through the heat transfer tubes and the air flowing outside. The present invention can also be applied to a device that performs heat exchange at.

Claims (22)

A heat exchanger having fins mounted in an indoor unit of an air conditioner in which a case body having a suction port at a front side and a blower outlet at a bottom side, respectively, and a permeation blower accommodated in the case body, are formed of a wind circuit, A front side heat exchanger and a rear side heat exchanger disposed in the middle of the wind circuit from the inlet to the perfusion blower or in the middle of the wind circuit from the perfusion blower to the blower outlet, The front side heat exchanger and the back side heat exchanger are each composed of a plurality of fins arranged in parallel at predetermined intervals and a gas flow therebetween, and a plurality of heat transfer tubes inserted at right angles to the fins and having a refrigerant flowing therein. Become, The fin in the front side heat exchanger is bent by two straight portions whose upstream leading edges and downstream trailing edges each have the same obtuse angle and one curved portion connecting between these two straight lines. In addition to forming The distance between the upstream leading edge and the downstream trailing edge in the region near the perfusion blower among the two regions fitted with the straight upstream leading edge and the straight downstream trailing edge of the pin formed in a bent shape. The heat exchanger with a fin characterized in that it is shorter than the distance of an upstream leading edge and a downstream trailing edge in the area | region far from a perfusion blower. The upstream side in the area | region far from a perfusion blower of Claim 1 WHEREIN: The distance of the upstream leading edge and the downstream trailing edge in the area | region near the perfusion blower is 20-23 mm, A finned heat exchanger, characterized in that the distance between the leading edge and the downstream trailing edge is 24 to 27 mm. The heat exchanger with a fin according to claim 1, wherein both curved portions on the upstream leading edge side and the downstream trailing edge side of the fin in the front side heat exchanger have the same shape. The heat exchanger with a fin of Claim 1 which made the curved part of the fin in the front side heat exchanger into arc shape. The upstream leading edge and the downstream trailing edge of the fin in the back side heat exchanger are configured in a straight line parallel to each other, and the distance between the upstream leading edge and the downstream trailing edge of the fin. Upstream leading edge and downstream trailing in the region far from the perfusion blower among the two regions sandwiched by the straight upstream leading edge of the fin and the straight downstream trailing edge of the fin in the front side heat exchanger. A finned heat exchanger, characterized in that it is equal to the distance of the edges. The heat transfer tube according to claim 1, wherein the heat transfer tube is inserted into a fin portion of a region far from the perfusion blower among two regions fitted by a linear upstream leading edge of the fin in the front side heat exchanger and a linear downstream trailing edge; The outer diameter of the heat exchanger tube inserted into the straight portion of the upstream leading edge of the fin and the straight portion of the downstream trailing edge of the rear side heat exchanger is 4 to 6.4 mm, and the heat direction along the mainstream direction of the gas. Heat exchanger tube is arranged in three rows, and the arrangement | positioning pitch of the unidirectional heat exchanger tube perpendicular | vertical to the mainstream direction of the said gas was 14.5-16 mm, The heat exchanger with a fin characterized by the above-mentioned. The heat transfer tube and rear surface of claim 6 inserted in a fin portion of a region far from a perfusion blower among two regions fitted with a straight upstream leading edge of the fin and a straight downstream trailing edge of the fin in the front side heat exchanger. The heat exchanger tube inserted into the linear part of the upstream leading edge of a fin in the side heat exchanger, and the part inserted by the linear part of the downstream trailing edge is comprised by the heat exchanger tube of two types of outer diameters, In addition, when the heat pipe of the larger outer diameter is arrange | positioned at the most upstream heat of gas flow, and when the said heat exchanger with a fin is used as a condenser or a gas cooler, it is used as a heat pipe near a refrigerant | coolant outlet, or as an evaporator. As a heat pipe near a refrigerant inlet, one pass is used, For heat transfer tubes with smaller outer diameter, when using the heat exchanger with fins as a condenser or gas cooler, when using as a heat transfer tube on the refrigerant upstream side or as an evaporator than the heat transfer tubes with larger outer diameter, A heat exchanger with fins, characterized in that the refrigerant flows in each of the heat transfer tubes downstream of the heat transfer tube using four passes. The heat transfer tube according to claim 1, wherein the heat transfer tube is inserted into a fin portion of a region near the perfusion blower among two regions fitted with a straight upstream leading edge of the fin and a straight downstream trailing edge of the fin in the front side heat exchanger; The outer diameter of the heat exchanger tube inserted into the portion of the region fitted into the curved upstream leading edge and the curved downstream trailing edge of the fin is 6.5 to 8.5 mm, respectively, in the column direction which becomes the direction along the mainstream direction of the gas. The heat exchanger with a fin was arranged in two rows, and the pitch of arrangement | positioning of the said heat exchanger tube of the unidirectional direction perpendicular to the mainstream direction of the said gas was 16-22 mm, The finned heat exchanger characterized by the above-mentioned. The flow of the gas according to claim 8, wherein the unidirectional arrangement pitch of the heat transfer pipe inserted into the portion of the region fitted between the curved upstream leading edge and the downstream curved trailing edge of the fin in the front side heat exchanger. A heat exchanger with a fin, characterized in that the upstream side of the column is equal to or less than the downstream side column. The fin part of the area | region near the perfusion blower among the two areas | intervals of the linear upstream leading edge of a fin in a front side heat exchanger, and a straight downstream trailing edge of a fin in the front side heat exchanger, and the said fin part. The heat exchanger tube respectively inserted into the part of the area | region fitted with the curved upstream leading edge and the downstream trailing edge of the curve consists of two types of heat exchanger tubes of the outer diameter, Furthermore, when the said heat pipe of the outer diameter is arrange | positioned in the most downstream row of gas flow, and when the said heat exchanger with a fin is used as a condenser or a gas cooler, it is used as a heat pipe near a refrigerant | coolant inlet, or an evaporator, Used as a heat transfer pipe near the refrigerant outlet, When using the heat exchanger with a fin as a condenser or a gas cooler, when using as a heat transfer tube of a refrigerant | coolant downstream side, or as an evaporator, when using the heat exchanger with a fin as a condenser or a gas cooler, a larger outer diameter A heat exchanger with fins, characterized in that the refrigerant flows using two passes, respectively, as a heat transfer tube on the upstream side of the refrigerant rather than the heat transfer tube. The finned heat exchanger according to claim 1, wherein the shortest distance between the heat transfer tube and the upstream leading edge or the downstream trailing edge of the fin is set to 1.8 mm or more. The two regions of claim 1, wherein when dehumidification operation is performed by dividing the reheater and the evaporator in one direction, the two regions sandwiched by a straight upstream leading edge of the fin and a straight downstream trailing edge of the fin in the front side heat exchanger. The region and the back side heat exchanger far from the mid-flow blower are used as the reheater, In the front side heat exchanger, of the two regions fitted with the straight upstream leading edge of the fin and the straight downstream trailing edge, the region near the perfusion blower and the upstream leading edge of the fin and the curved A finned heat exchanger, characterized in that it uses the region sandwiched by the downstream trailing edge as an evaporator. The plurality of cutoff portions according to claim 1, wherein the plurality of cutoff portions are formed on the fin surface between adjacent heat transfer tubes in a unidirectional direction, The rising portion near each heat transfer tube of each cut portion is formed in the direction along the circumference of the heat transfer tube, and the ratio of the widths between the cut portions adjacent in the column direction to the width of the heat direction of the cut portions is 2 to 2.5. A heat exchanger with a fin, characterized in that. The heat exchanger with a fin according to claim 13, wherein the height of the cutout portion is set to 1/4 to 3/4 of the pitch of adjacent fins. The height of the cut-out portion is set to 1/2 of the pitch between adjacent fins in the region where the wind speed with which the fin-attached heat exchanger approaches the perfusion blower is large. The heat exchanger with a fin characterized in that the other region is 3/4 of the pitch of adjacent fins. The pinned heat exchanger according to claim 13, wherein the shortest distance between the cutout portion and the upstream leading edge or the downstream trailing edge of the fin is set to 1.8 mm or more. The notch portion is formed in the direction along a unidirectional direction in the fin of the center part between the heat | fever of the said two heat exchanger tubes, when there exists a temperature difference between the refrigerant | coolants which flow inside between two heat exchanger tubes adjacent in a column direction. Heat exchanger with a fin, characterized in that. The method of claim 1, wherein when the dehumidification operation is performed by dividing the reheater and the evaporator in one direction, a notch portion is formed while leaving the uncut portion in the pin portion between the reheater region and the evaporator region. Heat exchanger with fins. The finned heat exchanger according to claim 1, wherein any one of HFC refrigerant, HC refrigerant, and carbon dioxide is used as the refrigerant flowing in the heat transfer tube. The heat exchanger with fins of Claim 1 manufactured with the upper end part of the fin in a front side heat exchanger, and the upper end part of the fin in a rear side heat exchanger connected, For a unidirectional direction perpendicular to the mainstream direction of the gas of a fin color for inserting a heat transfer tube formed in the fin in a state where the upper end of the fin in the front side heat exchanger and the upper end of the fin in the rear side heat exchanger are connected. About the pitch The finned heat exchanger of which the arrangement | positioning pitch of the fin color of the location adjacent to the boundary part of the said front side heat exchanger and said back side heat exchanger is made shorter than the arrangement pitch in another unidirectional direction. A method for manufacturing a heat exchanger with fins according to claim 1 comprising a front side heat exchanger and a back side heat exchanger, After laminating a plurality of fins obtained by successively pressing the fins in the state in which the upper end of the fin in the front side heat exchanger and the upper end of the fin in the back side heat exchanger are connected at the boundary portion, a plurality of fins are laminated. Let's And each fin is cut at the boundary between the front side heat exchanger and the back side heat exchanger and separated into the front side heat exchanger and the back side heat exchanger. A manufacturing method of a heat exchanger with a fin according to claim 20 having a front side heat exchanger and a back side heat exchanger, When the upper end part of the fin in the said front side heat exchanger and the upper end part of the fin in the said back side heat exchanger are continuously press-processed as one fin of the state connected at the boundary part, After stacking a plurality of fins formed with shorter pitches than the other unidirectional pitches for the unidirectionally adjacent portions of the fin color for inserting the heat transfer tubes into the front heat exchanger and the rear heat exchanger, respectively, Insert the heat pipe through the pin color, And then separating the fins into the front side heat exchanger and the back side heat exchanger.

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