CN203464829U - Heat-exchanger header box and heat exchanger therewith - Google Patents

Abstract

The utility model relates to a heat-exchanger header box and a heat exchanger therewith, wherein the refrigerating fluid of the heat-exchanger header box flows in a parallel manner in a plurality of flat tubes (30) which are configured in parallel. A header box (10) is provided with a plurality of through holes (12) which are arranged in parallel along the length direction and respectively connected with one end of the plurality of flat tubes (30). The header box (10) at least forms a space which is communicated with the plurality of through holes (12) and becomes a flow path of the refrigerating fluid. The through holes (12) are divided into inlet-side through holes and outlet-side through holes. The inlet-side through holes are respectively connected with an end part of a refrigerating fluid inlet side of the flat tubes (30). The outlet-side through holes are connected with an end part of a refrigerating fluid outlet side of the flat tubes (30). A plurality of grooves are formed along a width direction perpendicular to a length direction at a part opposite to the inlet-side through holes in the space, and extend along the length direction of the header box. Therefore, the heat-exchanger header box can restrain pressure loss, cannot impair the heat transfer performance of the heat exchanger, can uniformly distribute the refrigerating fluid, and is simple in structure.

Description

Header for heat exchanger and heat exchanger having the header for heat exchanger

technical field

The utility model relates to, for example, a header box for a heat exchanger used in a refrigeration cycle device such as an air conditioner, and a heat exchanger having the header box for a heat exchanger. the

Background technique

Conventionally, there is a heat exchanger in which a pair of headers extending in the vertical direction are arranged separately in the left-right direction, a plurality of flat tubes are arranged in parallel between the pair of headers, and the plurality of heat exchange tubes are arranged in parallel. Both ends communicate with a pair of header boxes. In this heat exchanger, when used as an evaporator, the refrigerant flows in as a gas-liquid two-phase flow, so that the liquid stays in the header on the inlet side in the direction of gravity, and the gas stays in the header on the other hand. above the inside of the tube box. Therefore, there is a problem that the refrigerant cannot be evenly distributed to the flat tubes, and the performance of the heat exchanger is lowered. the

Therefore, when the heat exchanger is used as the evaporator, the function of evenly distributing the refrigerant to the header on the inlet side is achieved. Conventionally, as a header having such a function, there is a header in which an annular flow path folded in the vertical direction is formed inside the header, and the flow of the two-phase refrigerant flowing in is circulated and uniformed inside the header. and distributed to each of a plurality of heat transfer tubes (for example, refer to Patent Document 1). the

【Existing technical literature】

[Patent Document 1] Japanese Patent Laid-Open No. 2011-85324 (Abstract, Figure 1)

Utility model content

Issues to be solved by utility models

However, in the header of Patent Document 1, since the refrigerant is led to the annular flow path, there is a problem that a pressure loss occurs and the heat transfer performance of the heat exchanger decreases. the

In addition, in the header of Patent Document 1, since it is necessary to separately form an annular flow path inside the header, there is a problem that the structure is complicated and the cost increases. the

The present invention was developed in view of such circumstances, and its object is to provide a heat exchanger with a simple structure that can suppress the pressure loss to a low level and distribute the refrigerant evenly without reducing the heat transfer performance of the heat exchanger. A header and a heat exchanger including the header for a heat exchanger. the

Technical solutions for solving problems

The content of the first aspect of the present invention is a header for a heat exchanger, which is a header for a heat exchanger in which a refrigerant flows in parallel in a plurality of heat transfer tubes arranged in parallel. , wherein, a plurality of through holes connected to one end of the plurality of heat transfer tubes are arranged side by side in the header along the length direction, and at least one of the through holes is formed in the header to communicate with the plurality of through holes and become a refrigerant The space of the flow path, the plurality of through holes are divided into an inlet side through hole and an outlet side through hole, the inlet side through hole is connected to the refrigerant inlet side end of the plurality of heat transfer tubes, the The outlet-side through hole is connected to the refrigerant outlet-side end of the heat transfer tube, and extends over the entire width direction perpendicular to the longitudinal direction at a portion opposing the inlet-side through hole in the space. A plurality of grooves are formed extending along the length of the header. the

The second aspect of the present utility model is based on the first aspect, the space is divided along the length direction of the header to form a plurality, and each of the plurality of spaces is classified as supplying water from the outside. Any one of the inflow space where the refrigerant flows in, the turn-back space that becomes the turn-back flow path, and the outflow space for the refrigerant to flow out to the outside, all the through holes communicating with the inflow space are inlet-side through holes. The plurality of grooves are formed on the whole of the length direction of the part of the inflow space, and the through holes communicating with the turn-back space are divided into an inlet side through hole group and an outlet side through hole group, and the through holes connected to the inlet side The plurality of grooves are formed on opposite parts of the group, all the through holes communicating with the outflow space are outlet-side through holes, and the plurality of grooves are not formed on the part forming the outflow space. the

A third aspect of the present invention is based on the second aspect, wherein the plurality of grooves are formed by the gaps between the protruding protrusions, and among the plurality of protrusions formed in the folding space The positions of the ends of the plurality of protrusions on the boundary side between the inlet-side through-hole group and the outlet-side through-hole group are staggered from each other in the protrusions adjacent in the width direction. the

A fourth aspect of the present utility model is based on the third aspect, wherein the plurality of grooves are formed by gaps between protruding protrusions, and the adjacent protrusions of the plurality of protrusions are different heights. the

A fifth aspect of the present invention is based on the fourth aspect, wherein the heights of the plurality of protrusions alternately rise and fall along the width direction. the

According to a sixth aspect of the present invention, in the fourth aspect, the heights of the plurality of protrusions are formed so as to increase toward a central portion in the width direction. the

The seventh aspect of the present utility model is based on any one of the first to third aspects, the header has a header body and a cover, the header body is in the shape of a box with one side open, The plurality of through holes are formed on a bottom surface opposite to the opening, and the cover is formed in a plate shape covering the opening. the

An eighth aspect of the present utility model is based on the seventh aspect, wherein the groove is formed on the cover. the

A ninth aspect of the present invention is a heat exchanger provided with the heat exchanger header according to any one of the first to eighth aspects. the

The content of the tenth aspect of the present utility model is a heat exchanger, wherein the heat exchange part has: a pair of header boxes for heat exchangers according to the second aspect or the third aspect, along the direction perpendicular to the air passing direction The directions are arranged separately from each other; a plurality of heat transfer tubes are arranged in parallel between the pair of heat exchanger headers, and both ends are connected to the plurality of through holes of the pair of heat exchanger headers; A plurality of fins are arranged to allow air to pass along the air passage direction, the heat exchanger has at least two heat exchange parts along the air passage direction, and the heat exchange parts are communicated with each other through straddling pipes , forming a refrigerant flow path in which the refrigerant passes from the inflow space to the outflow space in the plurality of heat transfer tubes of the heat exchange portion on the upstream side in the air passing direction, After flowing back and forth in the space, it flows into the heat exchange part on the downstream side in the direction of passage of air through the straddle piping, and similarly flows from the inflow space to the outflow space of the heat exchanger header. When the heat exchanger is used as an evaporator, the number of paths of the refrigerant flowing in the heat exchange part on the upstream side is greater than that of the refrigerant flowing in the heat exchange part on the downstream side. The number of paths is small. the

An eleventh aspect of the present invention is based on the ninth or tenth aspect, wherein the heat transfer tube is a flat tube having a plurality of through holes serving as refrigerant flow paths. the

The effect of utility models

According to the present invention, it is possible to obtain a header for a heat exchanger that can suppress pressure loss to a low level, that can distribute refrigerant evenly without reducing the heat transfer performance of the heat exchanger, and that has a simple structure. the

Description of drawings

FIG. 1 is a schematic perspective view of a heat exchanger 1 using a heat exchanger header according to Embodiment 1 of the present invention. the

FIG. 2 is a perspective view showing the flat tube 30 of FIG. 1 . the

FIG. 3 is an exploded perspective view of the inlet header 10 of FIG. 1 . the

Fig. 4 is an A-A sectional view of the inlet header portion of Fig. 1 . the

FIG. 5 is a diagram showing a refrigerant circuit of a refrigeration cycle device 50 employing the heat exchanger 1 of FIG. 1 . the

Fig. 6 is a diagram showing the flow of refrigerant when the heat exchanger 1 of Fig. 1 is used as an evaporator. the

FIG. 7 is a diagram showing a refrigerant flow state in the inlet header 10 . the

Fig. 8 is a B-B sectional view of Fig. 7 . the

FIG. 9A is a diagram showing an example of a refrigerant flow state in the header in the case of a header without grooves as a comparative example. the

9B is a diagram showing another example of the refrigerant flow state in the header in the case of a header without grooves as a comparative example. the

FIG. 10 is a diagram showing Modification 1 of the groove 14 of FIG. 3 . the

FIG. 11 is a diagram showing Modification 2 of the groove 14 of FIG. 3 . the

FIG. 12 is a diagram showing a heat exchanger 1A according to Embodiment 2 of the present invention. the

FIG. 13 is an exploded perspective view of the header 70 of FIG. 1 . the

FIG. 14A is a diagram showing a modified example of the groove 14 of FIG. 13 . the

FIG. 14B is a diagram showing another modified example of the groove 14 of FIG. 13 . the

15A is a diagram showing a heat exchanger 1B according to Embodiment 3 of the present invention, and is a schematic side view of the heat exchanger viewed from a direction perpendicular to the air passing direction indicated by a dotted arrow. the

15B is a diagram showing the heat exchanger 1B according to Embodiment 3 of the present invention, and is a schematic cross-sectional view of an upstream side heat exchange unit 1Ba on the upstream side with respect to the air passing direction. the

15C is a diagram showing the heat exchanger 1B according to Embodiment 3 of the present invention, and is a schematic cross-sectional view of the downstream side heat exchange part 1Bb on the downstream side with respect to the air passing direction. the

15D is a diagram showing the heat exchanger 1B according to Embodiment 3 of the present invention, and is a plan view of the heat exchanger. the

Explanation of reference signs

1 heat exchanger, 1A heat exchanger, 1B heat exchanger, 1Ba upstream heat exchange part, 1Bb downstream heat exchange part, 10 header (inlet header), 10A space, 10a refrigerant inlet piping, 11 Header body, 11a opening, 11b bottom, 12 through hole, 13 cover, 13a surface, 14 groove, 15 protrusion, 20 header (outlet header), 20a refrigerant outlet piping, 30 flat tube, 30a through hole, 40 fin, 50 refrigeration cycle device, 51 compressor, 52 condenser, 53 expansion valve, 54 evaporator, 70 header, 71 header main body, 71a opening, 71b bottom surface, 72 through hole, 73 partition, 74A cover, 74B cover, 74C cover, 80 header, 83 partition, 84D cover, 84E cover, 90 straddle piping, 100a refrigerant inlet piping, 200a refrigerant outlet piping, 700 headers, 703 partitions, 800 headers, A~H spaces. the

Detailed ways

Implementation mode 1

FIG. 1 is a schematic perspective view of a heat exchanger using a heat exchanger header according to Embodiment 1 of the present invention. In FIG. 1 and the drawings described later, components assigned the same reference numerals are the same or corresponding components, and are used in common throughout the specification. In addition, the forms of the constituent elements described in the entire specification are merely illustrative, and are not limited to these descriptions. the

The heat exchanger 1 is a parallel-flow heat exchanger in which refrigerant flows in parallel, and is particularly a one-way heat exchanger in which the refrigerant flows from one side to the other throughout the heat exchanger 1 . The heat exchanger 1 has: a pair of header boxes 10, 20 arranged separately from each other; a plurality of flat tubes (heat transfer tubes) 30, which are arranged in parallel between the pair of header boxes 10, 20; Tube boxes 10 , 20 connected; a plurality of fins 40 . A pair of headers 10, 20, flat tubes 30, and fins 40 are all made of aluminum or an aluminum alloy. the

The fin 40 is a plate-shaped fin that is stacked at a distance from each other between a pair of headers 10 and 20 , and air passes therebetween, and a plurality of flat tubes 30 penetrate therethrough. In addition, the fin 40 does not necessarily have to be a plate-shaped fin, and what is necessary is just to arrange|position the fin 40 so that air may pass along the air passage direction. For example, corrugated fins arranged alternately with the flat tubes 30 in the vertical direction may be used. The point is that the fins arranged to allow air to pass in the air passing direction may be sufficient. the

As shown in FIG. 2 , the flat tube 30 has a plurality of through holes 30 a serving as refrigerant flow paths. In addition, the heat transfer tubes are not limited to flat tubes, and circular tubes or other arbitrary shapes may be used. the

A refrigerant inlet pipe 10 a is connected to the inlet header 10 on the refrigerant inlet side of the plurality of flat tubes 30 among the pair of headers 10 and 20 , and a refrigerant inlet pipe 10 a is connected to an outlet on the refrigerant outlet side of the plurality of flat tubes 30 . A refrigerant outlet pipe 20 a is connected to the header 20 . the

The characteristic of the present invention is the header of the inlet side (hereinafter referred to as the inlet header 10 ) among the pair of headers 10 , 20 , and its structure will be described below with reference to FIG. 3 . the

FIG. 3 is an exploded perspective view of the inlet header 10 of FIG. 1 . Fig. 4 is an A-A sectional view of the inlet header portion of Fig. 1 . the

The inlet header 10 has a box-shaped header body 11 with one surface open and a plate-shaped cover 13 covering the opening 11a of the header body 11, and a refrigerant flow path is formed between them. At least one space 10A. In the header main body 11 , a plurality of through-holes 12 as inlet-side through-holes are arranged in parallel along the longitudinal direction of the header main body 11 on the bottom surface 11 b facing the opening 11 a. Ends on the refrigerant inlet side of the plurality of flat tubes 30 are connected to the plurality of through holes 12 to communicate in the space 10A. In addition, a refrigerant inlet pipe 10 a is connected to the inlet header 10 . the

In addition, in the cover body 13, a plurality of grooves 14 extending in the longitudinal direction are formed over the entire width direction perpendicular to the longitudinal direction, and these grooves 14 are formed on the surface facing the through hole 12 in at least one space 10A. 13a on. Specifically, the groove 14 is formed by gaps between the plurality of protrusions 15 protruding from the cover body 13 . The groove 14 is provided for the operation of introducing the refrigerant liquid flowing into the inlet header 10 into the groove by the action of surface tension, and uniformly distributing the refrigerant from the inlet header 10 to each path. . the

When manufacturing the inlet header 10 configured in this way, the box-shaped header main body 11 is formed by cutting or the like, and the through-hole 12 is formed in the header main body 11 . In addition, the cover body 13 is formed by cutting or the like. The lid body 13 is configured to be fittable so as to be temporarily fixed to the opening 11 a of the header body 11 , and solder is applied to the fitting portion. the

Furthermore, when manufacturing the entire heat exchanger 1, the cover body 13 is fitted and temporarily fixed to the opening 11a of the header main body 11, and the outlet header 20, the flat tubes 30, and the fins 40 are all assembled. Simultaneously, the whole body is brazed. the

FIG. 5 is a diagram showing a refrigerant circuit of a refrigeration cycle device 50 employing the heat exchanger 1 of FIG. 1 . the

The refrigeration cycle device 50 has a compressor 51 , a condenser 52 , an expansion valve 53 as a decompression device, and an evaporator 54 . At least one of the condenser 52 and the evaporator 54 uses the heat exchanger 1 . The gas refrigerant discharged from the compressor 51 flows into the condenser 52, exchanges heat with the air passing through the condenser 52, and flows out as high-pressure liquid refrigerant. The high-pressure liquid refrigerant flowing out of the condenser 52 is decompressed by the expansion valve 53 to become a low-pressure gas-liquid two-phase refrigerant, and flows into the evaporator 54 . The low-pressure gas-liquid two-phase refrigerant flowing into the evaporator 54 exchanges heat with the air passing through the evaporator 54 to become a low-pressure gas refrigerant, which is sucked into the compressor 51 . the

Fig. 6 is a diagram showing the flow of refrigerant when the heat exchanger 1 of Fig. 1 is used as an evaporator. the

The gas-liquid two-phase refrigerant flowing out of the expansion valve 53 flows into the inlet header 10 through the refrigerant inlet pipe 10 a. The refrigerant that has flowed into the inlet header 10 flows from one end to the other end of each flat tube 30 constituting each path of the heat exchanger 1 , joins in the outlet header 20 , and flows from the refrigerant outlet pipe 20 a to the outside. flow out. the

Next, the operation inside the inlet header will be described. FIG. 7 is a diagram showing a refrigerant flow state in the inlet header 10 . FIG. 8 is a cross-sectional view taken along line B-B of FIG. 7 , and is a schematic diagram showing a state in which liquid refrigerant accumulates between the tanks in the inlet header 10 . FIG. 9A is a diagram showing an example of the flow state of the refrigerant in the header in the header in which the tank 14 is not provided as a comparative example. FIG. 9B is a diagram showing another example of the flow state of the refrigerant in the header in the header in which the tank 14 is not provided as a comparative example. the

First, the flow state of the refrigerant in the comparative example will be described with reference to FIGS. 9A and 9B . When the amount of refrigerant circulating in the refrigerant circuit is large, the gas-liquid two-phase refrigerant flowing into the inlet header 10 from the refrigerant inlet pipe 10a accumulates in the inlet header due to the driving force at the time of inflow as shown in FIG. 9A . The upper part of the box 10. On the other hand, when the amount of refrigerant circulating in the refrigerant circuit is small, the liquid refrigerant in the gas-liquid two-phase refrigerant flowing into the inlet header 10 from the refrigerant inlet pipe 10a stays at the inlet due to the influence of gravity. The lower part of the header 10. In the case of such a structure in which the inlet header 10 is not provided with the groove 14, the liquid refrigerant concentrates on the upper part or the lower part, and the distribution to each path becomes uneven. the

Hereinafter, the flow state of the refrigerant in the inlet header 10 of the present embodiment will be described with reference to FIGS. 7 and 8 . The gas-liquid two-phase refrigerant flowing into the inlet header 10 from the refrigerant inlet pipe 10a flows in the inlet header 10, and the liquid refrigerant is introduced into the tank 14 by the action of surface tension. Therefore, the liquid refrigerant is held uniformly in the longitudinal direction in the inlet header 10, and the amount of liquid refrigerant flowing into each of the flat tubes 30 is averaged. the

As described above, according to the first embodiment, by providing the plurality of grooves 14 in the cover body 13 and acting on the surface tension, the drift of the liquid refrigerant can be suppressed, and the refrigerant can be evenly distributed and flowed into the plurality of flat tubes 30 . among each other. Therefore, the heat exchange efficiency can be improved, and the capacity when the heat exchanger 1 is used as an evaporator can be maximized. the

In addition, the present Embodiment 1 utilizes the surface tension effect of the liquid refrigerant to prevent uneven refrigerant distribution, thereby suppressing pressure loss and suppressing the use of the heat exchanger 1 as an evaporator compared with conventional structures. The performance of the case is degraded. the

In addition, the inlet header 10 of the first embodiment is composed of a header main body 11 and a cover body 13 having a groove 14 , and has a simple structure, thereby being easy to manufacture and achieving cost reduction. the

In addition, the inlet header of this invention is not limited to the structure shown in FIG. 3, In the range which does not deviate from the summary of this invention, it can implement variously, for example as following (1), (2). the

(1) FIG. 10 is a diagram showing Modification 1 of the groove 14 in FIG. 3 . the

In the structure of the groove 14 of the present embodiment shown in FIG. 5, the heights of the protrusions 15 are all the same, but as shown in FIG. 10 in the up and down direction) alternately high and low structure. In the case of such a configuration, the end surface (inclined surface) of the flat tube 30 side of the groove 14 (shown by the dotted line 14a in FIG. 10 ) is wider than the height-aligned structure as shown in FIG. effect of the refrigerant. In addition, the height of the protrusions 15 is not limited to the structure that alternately changes in length, and the same effect can be expected as long as the heights of the protrusions 15 adjacent to each other in the width direction of the cover body 13 are shifted from each other. As another example of the configuration in which the heights of the protrusions 15 adjacent to each other in the width direction of the lid body 13 are shifted from each other, the following Modification 2 may be employed. the

(2) FIG. 11 is a diagram showing Modification 2 of the groove 14 in FIG. 3 . the

The action of retaining the refrigerant in the groove 14 due to the surface tension makes the groove 14 narrower in width (length in the vertical direction in FIG. 11 ), and the higher the height of the groove 14, the wider the width becomes. In addition, the liquid refrigerant flowing into the inlet header 10 tends to stagnate at both ends of the cover 13 in the width direction. Therefore, in Modification 2, the protrusion 15 is formed so that the height of the protrusion 15 becomes higher as it goes from both end portions in the width direction to the center portion, and the height of the groove 14 is adjusted so that the refrigerant is retained as it goes toward the center portion in the width direction. force becomes stronger. Thereby, the refrigerant drift can be suppressed also in the width direction, and the amount of refrigerant in each groove 14 can be averaged in both the longitudinal direction and the width direction. As a result, the refrigerant can be expected to be more evenly distributed among the flat tubes 30 . In addition, here, an example in which only the height of the groove 14 is changed is shown, but the width of the groove 14 may be narrowed toward the center. the

As described above, the feature of the present invention is that the inlet header 10 is provided with a plurality of grooves 14 . Furthermore, as the heat exchanger 1 employing this feature, in Embodiment 1, an example of a one-way flow path type heat exchanger in which the refrigerant flows from one to the other in the entire heat exchanger is shown, However, it can also be applied to a turn-back channel type heat exchanger that flows while turning the channel back halfway. Next, in the following Embodiment 2 and Embodiment 3, a configuration in which the present invention is applied to a return flow path type heat exchanger will be described. the

Implementation mode 2

FIG. 12 is a diagram showing a heat exchanger 1A according to Embodiment 2 of the present invention. the

The heat exchanger 1A is a parallel-flow heat exchanger in which refrigerant flows in parallel, and is particularly a return flow path type heat exchanger. In addition, a configuration example in which the number of paths is five is shown here. the

The heat exchanger 1A has: a pair of headers 70 , 80 arranged separately from each other; a plurality of (here, 20) flat tubes (heat transfer tubes) 30 arranged in parallel between the pair of headers 70 , 80 , both ends are connected with a pair of header boxes 70, 80; a plurality of fins 40. A pair of headers 70, 80, flat tubes 30, and fins 40 are all made of aluminum or an aluminum alloy. The structures of the flat tubes 30 and the fins 40 are the same as those of the first embodiment. the

FIG. 13 is an exploded perspective view of the header 70 of FIG. 1 . the

The header 70 has a box-shaped header body 71 with one surface open. On the bottom surface 71 b facing the opening 71 a of the header body 71 , a plurality of through holes 72 connected to the plurality of flat tubes 30 are arranged in parallel along the longitudinal direction of the header body 71 . In addition, two partitions 73 are provided inside the header main body 71 to form three independent spaces A, B, and C that communicate with the plurality of through holes 12 and serve as refrigerant flow paths, and are respectively covered by the cover body 74A. , 74B, 74C are closed. the

The flow of the refrigerant in the heat exchanger 1A will be described later, but in the cover bodies 74A, 74B, and 74C, the end portions of the flat tubes 30 on the refrigerant inlet side are formed with the same structure as that of the first embodiment. Multiple slots 14 for the role. Hereinafter, a specific description will be given. the

The space A is an inflow space for the refrigerant from the outside to flow in, and the ends of the flat tubes 30 on the refrigerant inlet side are connected to the plurality of through-holes 72 communicating with the space A, so that they are integrally formed in the cover body 74A. There are slots 14. In addition, the space B is a turn-back space serving as a turn-back flow path, and the end of the refrigerant inlet side of the flat tube 30 is connected to the upper half of the plurality of through holes 72 communicating with the space B, and the flat tube 30 is connected to the lower half. 30 on the refrigerant outlet side, the groove 14 is provided in the upper half of the cover 74B. In addition, the space C is an outflow space for the refrigerant to flow out to the outside, and the plurality of through holes 72 communicating with the space C are connected to the end of the flat tube 30 on the refrigerant outlet side, so the groove 14 is not provided in the cover 74C. In addition, hereinafter, among the plurality of through holes 72 , the through hole connected to the end of the flat tube 30 on the refrigerant inlet side may be referred to as an inlet side through hole, and the end connected to the end of the flat tube 30 on the refrigerant outlet side may be referred to as an inlet side through hole. The through hole is called the outlet side through hole. the

On the other hand, as shown in FIG. 12 , one partition 83 is provided in the header 80 , and the interior is divided into two spaces D and E. As shown in FIG. Furthermore, like the header 70, the respective spaces D and E are closed by lids 84D and 84E, respectively. Also, in the lid bodies 84D and 84E, a plurality of grooves 14 are formed in portions of the flat tube 30 that face the inlet-side through holes in the same manner as described above. Specifically, a plurality of grooves 14 are formed in the upper half of each cover body 84D, 84E. the

When manufacturing the header 70 configured in this way, the header main body 71 is formed by cutting or the like, and the through-hole 72 is formed in the header main body 71 . In addition, the respective lid bodies 74A, 74B, and 74C are formed by cutting or the like. The lids 74A, 74B, and 74C are configured to be fittable so as to be temporarily fixed to the openings of the spaces A, B, and C of the header body 11 , and solder is applied to the fitting portions. The header 80 can also be manufactured similarly. the

Furthermore, when manufacturing the entire heat exchanger 1B, the lids 74A, 74B, and 74C are respectively fitted and temporarily fixed to the openings of the spaces A, B, and C of the header 70 , and the header 80 is also similarly The lids 84D, 84E are fitted and temporarily fixed to the openings of the respective spaces D, E, respectively. Then, in a state where all the flat tubes 30 and the fins 40 are assembled, the whole is simultaneously brazed and joined. the

Hereinafter, the flow of the refrigerant in the heat exchanger 1 will be described with reference to FIG. 12 . Here, the flow of the refrigerant when the heat exchanger 1 is used as an evaporator will be described. In FIG. 12 , solid arrows indicate the flow of refrigerant. the

The gas-liquid two-phase refrigerant flowing in from the refrigerant inlet pipe 10a flows into the space A, flows from one end of the flat tube group connected to the space A to the other end, and flows into the space D. The refrigerant that has flowed into the space D turns back here, flows from one end to the other end of another flat tube group connected to the space D, and flows into the space B. Then, the refrigerant that has flowed into the space B turns back here, flows from one end to the other end of another flat tube group connected to the space B, and flows into the space E. Then, the refrigerant that has flowed into the space E turns back here, and flows from one end of the other flat tube group connected to the space E to the other end. Then, the refrigerants flowing out from the other end join together in the space C, and flow out from the refrigerant outlet pipe 20a to the outside. the

In the flow of the above refrigerant, since the groove 14 is provided to face the end of each flat tube group on the refrigerant inlet side, the refrigerant is suppressed by the surface tension of the liquid refrigerant similarly to the first embodiment. The refrigerant is distributed from each space to each path approximately equally. the

As described above, according to the second embodiment, the same effect as that of the first embodiment can be obtained also in the return flow path type heat exchanger. the

In addition, in the second embodiment, the plurality of protrusions 15 formed on the lids 74B, 84D, and 84E of the spaces B, D, and E serving as the turned-back spaces employ an inlet-side through-hole group and an outlet-side through-hole group. The positions of the end portions on the boundary side between the groups are all aligned, but a structure as shown in FIGS. 14A and 14B below may also be employed. the

14A is a diagram showing a modified example of the groove 14 in FIG. 13 , and FIG. 14B is a diagram showing another modified example of the groove 14 in FIG. . the

As shown in FIG. 14A , among the plurality of protrusions 15 , positions of ends on the boundary side between the inlet-side through-hole group and the outlet-side through-hole group may be alternately shifted along the width direction of the cover. With such a configuration, the end surface of the groove 14 on the boundary side becomes an inclined surface, and the end surface is wider than the configuration in which the ends are aligned as shown in FIG. The positions of the ends of the protrusions 15 are not limited to such alternate configurations, and similar effects can be expected as long as the positions of the protrusions 15 adjacent to each other in the width direction of the cover are shifted. the

14B is another example of the structure in which the positions of adjacent projections 15 in the width direction of the cover are alternately shifted. Short, or although it is not shown in figure, the length of the longitudinal direction of the protrusion 15 may become long toward the center part of the width direction. the

In addition, the modification examples applied to the same components as those in the first embodiment are also similarly applied to the second embodiment. In addition, a configuration in which the modified example described in Embodiment 2 and the modified example described in Embodiment 1 may be combined is also possible. These points are also the same in Embodiment 3 described later. the

Implementation mode 3

Embodiment 3 corresponds to the structure in which the heat exchangers of the embodiment 2 are provided in multiple rows (here, two rows) along the direction of passage of air. the

15A, 15B, 15C, and 15D are diagrams showing a heat exchanger according to Embodiment 3 of the present invention. Fig. 15A is a schematic side view of the heat exchanger viewed from a direction perpendicular to the air passage direction indicated by the dotted arrow. 15B is a schematic cross-sectional view of the upstream side heat exchange unit 1Ba on the upstream side with respect to the air passing direction. 15C is a schematic cross-sectional view of the downstream side heat exchange unit 1Bb on the downstream side with respect to the air passing direction. Figure 15D is a top view of the heat exchanger. Hereinafter, the differences between the third embodiment and the second embodiment will be mainly described. the

The heat exchanger 1B includes the same heat exchanger 1A as in Embodiment 2 as an upstream heat exchange portion 1Ba, and further includes a downstream heat exchange portion 1Bb on the downstream side in the air passing direction. Furthermore, the upstream side heat exchange unit 1Ba and the downstream side heat exchange unit 1Bb are connected by a straddling pipe 90 . the

The downstream heat exchange part 1Bb is composed of 5 paths with respect to the upstream heat exchange part 1Ba, and the downstream heat exchange part 1Bb is composed of 10 paths which are more than the upstream heat exchange part 1Ba. The reason for changing the number of paths in the upstream heat exchange section 1Ba and the downstream heat exchange section 1Bb will be described later. The downstream side heat exchange part 1Bb is the same as the upstream side heat exchange part 1Ba except that the structure of the header part differs from the upstream side heat exchange part 1Ba. the

In the downstream side heat exchange part 1Bb, the number of partition plates of the header 700 connected with the straddling piping 90 is different from that of the upstream side heat exchange part 1Ba. One partition plate 703 is provided in the header 700, and the Two spaces F and G are formed. In addition, no partition plate is provided in the header 800, and one space H is formed as a whole. In addition, similarly to Embodiments 1 and 2, grooves 14 are provided in the headers 700 and 800 of the downstream side heat exchange unit 1Bb at portions facing the refrigerant inlet-side ends of the respective flat tubes 30 . the

Hereinafter, the flow of the refrigerant in the heat exchanger 1B will be described with reference to FIGS. 15A to 15D . Here, the flow of the refrigerant when the heat exchanger 1 is used as an evaporator will be described. In FIGS. 15A to 15D , solid line arrows indicate the flow of refrigerant. the

The flow of the refrigerant in the heat exchanger 1B is the same as that in Embodiment 2 regarding the upstream side heat exchange unit 1Ba. Then, the refrigerant flowing out from the refrigerant outlet pipe 20 a of the upstream side heat exchange portion 1Ba flows into the space F of the downstream side heat exchange portion 1Bb from the refrigerant inlet pipe 100 a via the straddle pipe 90 . The refrigerant that has flowed into the space F flows from one end of the flat tube group communicating with the space F to the other end, and flows into the space H. Then, the refrigerant that has flowed into the space H turns back here, and flows from one end to the other end of another flat tube group connected to the space H. Then, the refrigerants flowing out from the other end join together in the space G, and flow out from the refrigerant outlet pipe 200a to the outside. the

In the flow of the above refrigerant, since the groove 14 is provided to face the end of each flat tube group on the refrigerant inlet side, similarly to Embodiments 1 and 2, the surface tension of the liquid refrigerant suppresses the flow of the refrigerant. In the biased flow of the refrigerant, the refrigerant is distributed approximately equally from each space to each path. the

Hereinafter, the reasons why the number of paths are changed in the upstream heat exchange section 1Ba and the downstream heat exchange section 1Bb will be described. the

When the heat exchanger 1B is used as an evaporator, the refrigerant flows in in a gas-liquid two-phase state, and finally flows out as a gas refrigerant, and the dryness increases toward the second half of the flow path. When the dryness is low, since the pressure loss when passing through the flow path is small, it is preferable to increase the flow rate of the refrigerant and increase the heat transfer rate. On the other hand, when the degree of dryness is high, since the pressure loss when passing through the channels is large, it is preferable to slow down the flow rate of the refrigerant, and the greater the number of channels, the slower the flow rate of the refrigerant. the

In the upstream side heat exchange part 1Ba corresponding to the first half of the flow path in the heat exchanger 1B, since the dryness of the refrigerant is low, the number of paths is reduced to increase the flow rate of the refrigerant to increase the thermal conductivity. On the other hand, in the downstream side heat exchange part 1Bb corresponding to the second half of the flow path, since the dryness becomes higher, the number of paths is increased to reduce the flow rate of the refrigerant to reduce the pressure loss. the

As described above, according to Embodiment 3, the same effects as Embodiments 1 and 2 are obtained, and the heat exchange capability can be improved by adopting a multi-row structure. In addition, since the flow rate of the refrigerant is increased by reducing the number of paths on the upstream side in the direction of passage of air with a low dryness of the refrigerant, the heat transfer rate is improved, and thus the heat exchange capability can also be improved in this regard. the

In addition, in Embodiment 3, a two-column structure was described, but a three or more-column structure may also be employed. the

In addition, in each of the above-mentioned embodiments, an example in which the outer shape of the header is a square shape was shown, but it is not limited to a square shape, and may be a cylindrical shape. In addition, when employing a plurality of rows as in Embodiment 3, it is preferable to adopt a square shape from the viewpoint of securing a size required as a header and realizing interference between rows. the

Claims (11)

1. A header box for a heat exchanger, which is a header box for a heat exchanger that makes refrigerant flow in parallel in a plurality of heat transfer tubes arranged in parallel, characterized in that, A plurality of through holes connected to one end of the plurality of heat transfer tubes are arranged side by side in the header along the length direction, The header box forms at least one space that communicates with the plurality of through holes and becomes a refrigerant flow path, The plurality of through holes are divided into inlet-side through-holes and outlet-side through-holes, the inlet-side through-holes are connected to the refrigerant inlet-side ends of the plurality of heat transfer tubes, the outlet-side through-holes are connected to The ends of the heat transfer tubes on the refrigerant outlet side are connected, A plurality of grooves extending in the longitudinal direction of the header are integrally formed in a portion of the space opposed to the inlet-side through hole across a width direction perpendicular to the longitudinal direction. the 2. heat exchanger header box as claimed in claim 1, is characterized in that, A plurality of the spaces are divided along the longitudinal direction of the header, and each of the plurality of spaces is classified into an inflow space into which refrigerant from the outside flows, a return space serving as a return flow path, Any one of the outflow spaces for the refrigerant to flow out to the outside, All the through-holes communicating with the inflow space are inlet-side through-holes, and the plurality of grooves are formed on the entire length direction of the portion forming the inflow space, The through-holes communicating with the turn-back space are divided into an inlet-side through-hole group and an outlet-side through-hole group, and the plurality of grooves are formed on a portion opposite to the inlet-side through-hole group, All the through-holes communicating with the outflow space are outlet-side through-holes, and the plurality of grooves are not formed in the portion where the outflow space is formed. the 3. The heat exchanger header according to claim 2, wherein the plurality of grooves are formed by gaps between protruding protrusions, and the plurality of grooves formed in the turn-back space are formed by gaps between each other. Among the protrusions, the positions of the ends of the plurality of protrusions on the boundary side between the inlet-side through-hole group and the outlet-side through-hole group are closer to the protrusions adjacent in the width direction. staggered from each other. the 4. The heat exchanger header according to any one of claims 1 to 3, wherein the plurality of grooves are formed by gaps between protruding protrusions, and the plurality of protrusions The heights of the adjacent protrusions of each portion are different from each other. the 5 . The header for a heat exchanger according to claim 4 , wherein the heights of the plurality of protrusions alternately rise and fall along the width direction. 6 . the 6 . The heat exchanger header according to claim 4 , wherein the heights of the plurality of protrusions are formed so as to increase toward a central portion in the width direction. 6 . the 7. The header box for a heat exchanger according to any one of claims 1 to 3, wherein the header box has a header body and a cover body, and the header body is open on one side. The box shape has the plurality of through holes formed on the bottom surface opposite to the opening, and the cover body is formed in a plate shape covering the opening. the 8. The heat exchanger header according to claim 7, wherein the groove is formed in the cover. the 9 . A heat exchanger comprising the heat exchanger header according to claim 1 . the 10. A heat exchanger, characterized in that, The heat exchange unit has: a pair of heat exchanger headers according to claim 2 or 3, arranged separately from each other in a direction perpendicular to the air passing direction; a plurality of heat transfer tubes arranged in parallel in the pair of headers. Between the heat exchanger headers, both ends are connected to the plurality of through holes of a pair of heat exchanger headers; a plurality of fins are arranged along the air passing direction for air to pass through, The heat exchanger has at least two heat exchange parts along the air passing direction, and the heat exchanging parts are connected to each other through straddling pipes to form the following refrigerant flow path, that is, the refrigerant flows in the air passing direction In the plurality of heat transfer tubes of the heat exchange section on the upstream side, after turning back in the turn-back space from the inflow space to the outflow space, the air flows in the passage direction through the straddle piping. The heat exchange part on the downstream side similarly flows from the inflow space to the outflow space of the heat exchanger header, turning back in the turning back space, When the heat exchanger is used as an evaporator, the number of refrigerant paths flowing through the heat exchange portion on the upstream side is smaller than the number of paths for refrigerant flowing through the heat exchange portion on the downstream side. the 11. The heat exchanger according to claim 9 or 10, wherein the heat transfer tube is a flat tube having a plurality of through holes serving as refrigerant flow paths. the

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