JP2006125652A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger comprising a refrigerant distributor capable of properly executing its refrigerant distributing function with a simple constitution and realizing cost reduction and space saving. <P>SOLUTION: This heat exchanger comprising the refrigerant distributor 4 for distributing and supplying a refrigerant to a plurality of prescribed flow channel portions in a heat exchanger main body having a refrigerant flow channel, is provided with a plate-shaped distributing member composed of center plates 7A, 7B having refrigerant dividing portions 9 for dividing the refrigerant from a refrigerant inflow port, and refrigerant branching flow channel portions 10a, 10b having refrigerant throttling function for supplying the refrigerant divided by the refrigerant dividing portions 9 to the plurality of prescribed flow channel portions in the heat exchanger main body by a predetermined flow rate; and the refrigerant distributor 4 is constituted of the platy members including the platy distributing members and overlapped with each other. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a heat exchanger, and more particularly to a heat exchanger that includes a refrigerant distributor and is used in an air conditioner or a refrigerator.

  As means for improving the heat transfer performance of the heat exchanger, a thin heat transfer tube or a flat tube having a plurality of microchannels is applied. However, when a heat transfer tube is thinned or a flat tube is applied, the cross-sectional area of the heat transfer tube is reduced, and the pressure loss of the refrigerant flowing in the heat transfer tube increases, so it is necessary to increase the number of flow paths through which the refrigerant flows. is there. Further, when the refrigerant flow path is increased, the refrigerant flows in a state where the refrigerant gas and the refrigerant liquid are mixed (gas-liquid two-phase state), so that a refrigerant distributor for uniformly distributing the refrigerant is required. Furthermore, when a refrigerant distributor is used, the cost increases and the installation space increases, so it is necessary to reduce the cost and save the space of the refrigerant distributor.

In a conventional refrigerant distributor, a plurality of narrow tube connection holes parallel to the axis of the member connecting the thin tubes are processed, and the flow tube connection hole and the circular recess are formed on the member connecting the flow tube. Are formed by surrounding them with a copper mantle member having good ductility (see, for example, Patent Document 1).
Thereby, even when the number of thin tubes for adjusting the flow rate of the refrigerant flowing through each branch flow path is large, it can be manufactured easily and at low cost.

In another conventional refrigerant distributor, a refrigerant inlet part into which refrigerant flows, a branch flow path connecting the refrigerant inlet part and a plurality of inlet parts of the heat exchanger, and a plurality of outlet parts of the heat exchanger are connected. An under plate having a refrigerant collecting groove, a refrigerant branching portion provided with a plurality of branch passages communicating with the refrigerant inlet portion and extending radially from the center thereof, and an over having a refrigerant collecting groove corresponding to the refrigerant collecting groove A plate and a lid that covers the refrigerant distribution portion of the overplate are provided, and the underplate and the overplate and the overplate and the lid are brazed and joined (for example, see Patent Document 2).
Thereby, the change of the refrigerant distribution number is facilitated, and the brazing reliability is improved.

Japanese Patent No. 2750272 JP 2000-220914 A

The conventional refrigerant distributor disclosed in Patent Document 1 needs to use a thin tube (hereinafter referred to as a capillary tube) for connecting the distributor and the heat exchanger and adjusting the amount of refrigerant flowing through each branch flow path. It was. Moreover, since the volume of the refrigerant distributor is large, there is a problem that the installation space becomes large.
Further, another conventional refrigerant distributor shown in Patent Document 2 has a plurality of branch flow paths, but each branch flow path has a wide width, and only serves to connect the refrigerant distribution section to the heat transfer tube. Therefore, the capillary tube function for adjusting the refrigerant flow rate was not provided.

  The present invention has been made to solve the above-described problems, and includes a refrigerant distributor that can accurately perform a refrigerant distribution function with a simple configuration, and that can realize cost reduction and space saving. It is intended to obtain a heat exchanger.

  In the heat exchanger according to the present invention, in the heat exchanger including a refrigerant distributor that distributes and supplies the refrigerant to a plurality of predetermined flow path portions in the heat exchanger body, the refrigerant that divides the refrigerant from the refrigerant inlet A plate-like distribution member having a branching flow path portion for supplying the flow-divided portion and the refrigerant branched by the refrigerant flow-dividing portion at a predetermined flow rate to a plurality of predetermined flow path portions in the heat exchanger main body; The refrigerant distributor is constituted by a plurality of plate-like members that are superposed on each other including the shape-like distribution member.

  According to the present invention, it is possible to obtain a heat exchanger equipped with a refrigerant distributor that can accurately perform a refrigerant distribution function with a simple configuration, and that can realize cost reduction and space saving.

Embodiment 1 FIG.
A first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a perspective view for explaining a state when a heat exchanger provided with a refrigerant distributor in Embodiment 1 is installed in an indoor unit for air conditioning. FIG. 2 is an exploded perspective view showing the configuration of the refrigerant distributor in the first embodiment. FIG. 3 is a side view for explaining the operation of the refrigerant flowing through the refrigerant distributor in the first embodiment. FIG. 4 is an enlarged cross-sectional view taken along line IV-IV in FIG. FIG. 5 is an exploded perspective view showing the configuration of the refrigerant distributor for explaining a modification of the first embodiment. FIG. 6 is an exploded perspective view showing the configuration of the refrigerant distributor for explaining another modification of the first embodiment. FIG. 7 is an exploded perspective view showing a configuration of a refrigerant distributor for explaining still another modified example of the first embodiment.

  As shown in FIG. 1, the refrigerant distributor 4 is installed along the side surface 2 a of the heat exchanger body 2 inside the air conditioning indoor unit 1. The air 23 as the heat exchange target flows in from the front surface of the heat exchanger body 2, exchanges heat inside the heat exchanger body 2, and then blows downward by the cross flow fan 3. Here, it is assumed that the speed of the heat exchange target air 23 flowing into the heat exchanger body 2 is equal at any position.

As shown in FIG. 2, the refrigerant distributor 4 includes, for example, a plate layer composed of three layers of under plates 6A and 6B, center plates 7A and 7B, and over plates 8A and 8B. Here, a configuration in which the refrigerant distributor 4 includes two refrigerant distributor units 4A and 4B is shown.
The under plate 6A, the center plate 7A, and the over plate 8A are superposed on each other to form a refrigerant distributor unit 4A, and the under plate 6B, the center plate 7B, and the over plate 8B are superposed on each other to form a refrigerant. A distributor unit 4B is configured.

The under plates 6A and 6B, the center plates 7A and 7B, and the over plates 8A and 8B constituting the refrigerant distributor units 4A and 4B respectively extend along the end surface 2a of the heat exchanger body 2, and The edge portion FG faces the circumferential surface 3a of the motor 3 that rotates the cross flow fan or the cross flow fan.
A cross flow fan is provided on an edge portion FG of the under plate 6A, 6B, the center plate 7A, 7B, and the cross flow fan of the over plates 8A, 8B or the peripheral portion 3a of the motor 3 that rotates the cross flow fan. Or the notch 14 for not interfering with the motor 3 which rotates a cross flow fan is provided.

  The under plates 6A and 6B, the center plates 7A and 7B, and the over plates 8A and 8B are arranged so as to extend on a plane orthogonal to the axis of the cross flow fan 3, respectively. The under plate 6A, the center plate 7A, and the over plate 8A The refrigerant distributor unit 4A configured by the above and the refrigerant distributor unit 4B configured by the under plate 6B, the center plate 7B, and the over plate 8B are coupled to each other in a link shape bent in the same plane. 4 is configured. The refrigerant distributor 4 faces the peripheral surface 3a of the motor 3 that rotates the cross flow fan or the cross flow fan along the end surface of the heat exchanger main body 2 and the cross flow fan or the cross flow. It is arranged in a state where the space formed by the peripheral surface 3a of the motor 3 for rotating the fan and formed inside the indoor unit 1 for air conditioning is effectively used.

  The under plates 6A and 6B are provided with a refrigerant inflow hole 16 and an outflow hole 22. The diameter of the through hole of the inflow hole 16 is 3 mm or less, and is formed by, for example, burring. Moreover, the diameter of the outflow hole 22 is arbitrary, and is similarly formed by burring. Here, the burring process is a process in which a pilot hole is formed in a flat plate, a stretch effect is applied to the periphery of the flat plate, and the flange portion is formed by extending in a cylindrical shape.

The center plates 7A and 7B are provided with a refrigerant branching portion 9, refrigerant branching channel portions 10a and 10b, a heat exchanger inflow portion 11, a U bend portion 12, and a refrigerant gas junction portion 21. At this time, the refrigerant branching section 9 and the refrigerant branch flow path section 10 are sandwiched between the heat exchanger 2 and the crossflow fan or the motor 3 that rotates the crossflow fan when viewed from the direction parallel to the axis of the crossflow fan 3. Placed in the area. The center plates 7A and 7B can be formed using, for example, press working.
Here, the total length of the flow paths of the refrigerant branch flow path portions 10a and 10b, the flow path width of each flow path, and the bending angle of each flow path are equal. For example, in the first embodiment, the bending angle of the refrigerant branching channel portion 10a is one 45 degree bending, three 90 degree bendings, and the total bending angle is 315 degrees, The bending angle of the part 10b is one 45 degree bending, one 180 degree bending, one 90 degree bending, and the total bending angle is 315 degrees.

A plurality of rows of heat transfer tube connecting portions 13a, 13b, 13c, and 13d are formed on the over plates 8A and 8B. The heat transfer tube connecting portions 13a, 13b, 13c, and 13d are formed by, for example, the burring process described above.
The heat transfer tube connecting portion 13a corresponds to the heat exchanger inflow portion 11 provided in the center plates 7A and 7B, communicates therewith, and distributes the refrigerant from the heat exchanger inflow portion 11 to the heat transfer tube 18a. It is.
Further, the heat transfer tube connecting portion 13d corresponds to the heat transfer tube outlet 17 provided in the center plates 7A and 7B, communicates therewith, and distributes the refrigerant from the heat transfer tube outlet 17 to the junction portion 21. The heat transfer tube connecting portions 13b and 13c correspond to the U vent portion 12 provided on the center plates 7A and 7B and communicate with the U vent portion 12 so that the refrigerant from the heat transfer tube 13b communicates with the heat transfer tube 13c.

  For the under plates 6A and 6B, the center plates 7A and 7B, and the over plates 8A and 8B, for example, a center plate is made of a brazing sheet coated with a brazing material on both sides and brazed using a continuous heat treatment furnace. Can be joined. In this manner, when the under plates 6A and 6B, the center plates 7A and 7B, and the over plates 8A and 8B are joined, a refrigerant flow path as shown in FIGS. 3 and 4 can be formed.

The refrigerant branch flow path portions 10a and 10b provided in the center plates 7A and 7B are formed on the surface of the center plates 7A and 7B on the side where they overlap with the under plates 6A and 6B.
The dimension in the depth direction in the flow path of the refrigerant branch flow path portions 10a and 10b provided in the center plates 7A and 7B is regulated by the surface of the under plates 6A and 6B that overlap and contact the center plates 7A and 7B. Combined with the setting of the dimensions, the cross-sectional shape of the flow path in the refrigerant branch flow path portions 10a and 10b is determined.

The flow paths of the refrigerant branch flow path portions 10a and 10b provided in the center plates 7A and 7B can be formed on the surface of the center plates 7A and 7B on the side where they overlap with the over plates 8A and 8B.
In this case, the dimension in the depth direction in the flow path of the refrigerant branch flow path portions 10a and 10b provided in the center plates 7A and 7B is determined by the surface of the overplates 8A and 8B that are superposed and contact with the center plates 7A and 7B. It is regulated and the cross-sectional shape of the flow path in the refrigerant branch flow path portions 10a and 10b is determined in combination with the setting of the width direction dimension.

  Next, operation | movement of a refrigerant | coolant is demonstrated using FIG. 3 and FIG. When the heat exchanger body 2 operates as an evaporator, for example, the refrigerant 19 is branched into two before flowing into the refrigerant distributor 4 and is provided in the refrigerant distributor units 4A and 4B in a gas-liquid two-phase state. It flows into the inflow hole 16 at the location. For example, the two branches before flowing into the inflow hole 16 have a simple structure in which the pipes are abutted, but here, the refrigerant branch flow path portions 10a provided in the two refrigerant distributor units 4A and 4B, Since the numbers 10b are equal, the flow resistances of the refrigerant distributor units 4A and 4B are equal, and the flow rate variation when the refrigerant 19 is bifurcated is reduced.

The refrigerant that has flowed into the inflow holes 16 provided in the under plates 6A and 6B constituting the refrigerant distributor units 4A and 4B passes through the inflow holes 16 because the diameter of the through holes of the inflow holes 16 is as small as 3 mm or less. In this state, the flow velocity is increased, and the refrigerant gas and the refrigerant liquid are uniformly mixed, and the refrigerants are respectively provided on the center plates 7A and 7B which are superposed on the under plates 6A and 6B and constitute the refrigerant distributor units 4A and 4B. The flow is diverted to the refrigerant branch flow path portions 10a and 10b by the diversion portion 9. The refrigerant branch flow passages 10a and 10b have a refrigerant throttling function equivalent to that of the capillary tube in the prior art, and accurately perform the refrigerant distribution function in place of the capillary tube in the prior art.
Here, with respect to the refrigerant branch flow path portions 10a and 10b, the length of each flow path, the width of each flow path, and the sum of the bending angles of each flow path are equal, so the flow resistance of each flow path becomes equal, The variation in the flow rate of the refrigerant flowing through the refrigerant branch flow path portions 10a and 10b is reduced.

The refrigerant that has passed through the flow paths of the refrigerant branch flow path portions 10 a and 10 b flows into the heat exchanger inflow portion 11.
As shown in FIG. 4, the refrigerant 19 flows from the heat exchanger inflow portion 11 provided in each of the center plates 7A and 7B to the heat transfer tube 18a through the heat transfer tube connection portion 13a. Heat is exchanged with the air 23 through fins inside, and it gradually evaporates. The heat transfer tube 18a and the heat transfer tube 18b are connected at the end of the heat exchanger opposite to the refrigerant distributor units 4A and 4B, and the refrigerant 19 passes through the heat transfer tube 18b and again from the heat transfer tube connection portion 13b to the refrigerant distributor unit. It flows into 4A and 4B. The refrigerant 19 that has flowed into the refrigerant distributor units 4A and 4B again passes through the U-bend portions 12 provided in the center plates 7A and 7B, flows into the heat transfer tubes 18c from the heat transfer tube connection portions 13c, and then flows into the heat transfer tubes 18c. The heat is exchanged inside the heat exchanger body 2 while passing through.
Here, a refrigerant passage is formed by the U bend portion 12 so that predetermined portions of the heat transfer tubes 18b and 18c constituting the internal flow path of the heat exchanger body 2 communicate with each other, and the heat exchange action in the heat transfer tubes 18b and 18c is performed. An appropriate flow path is set for the refrigerant to be performed, and an appropriate state for ensuring high heat exchange efficiency in the heat exchanger body 2 is realized.
And the refrigerant | coolant 19 flows out from the heat exchanger tube exit 17 in the single phase state of refrigerant gas through the heat exchanger tube connection part 13d from the heat exchanger tube 18d, and is the refrigerant gas junction part 21 provided in center plate 7A, 7B, respectively. It merges with the refrigerant 19 that has passed through another refrigerant flow path. Thereafter, the refrigerant 19 flows out into the pipe connected to the heat exchanger body 2 from an outflow hole 22 provided in each of the under plates 6A and 6B and communicating with the refrigerant gas junction 21.
Further, when the heat exchanger body 2 operates as a condenser, the refrigerant flows in a direction opposite to that when the heat exchanger body 2 operates as an evaporator.

As described above, in the refrigerant distributor 4 shown in the first embodiment, the inflow hole 16 into which the refrigerant flows, the refrigerant distribution unit 9 that divides the refrigerant, and the heat as the inlet to the refrigerant distribution unit 9 and the heat exchanger main body 2. Refrigerant branch flow path portions 10a and 10b, which serve as substitutes for capillary tubes for connecting the exchanger inflow portion 11 and controlling the refrigerant flow rate, a U bend portion 12 for flowing the refrigerant through the heat exchanger body 2, and a refrigerant gas Since it has a confluence 21 and is integrally formed by a plate structure formed by joining two or more layers, the number of parts such as a capillary tube and a U-bend required for a conventional heat exchanger can be reduced. This can reduce the cost of the refrigerant distributor. Further, since the plate-like laminated structure is adopted, space saving can be realized. In particular, the dimension of T shown in FIG. 1 can be reduced.
In addition, when viewed from a direction parallel to the axis of the cross flow fan 3, an inflow hole 16, a refrigerant branching portion 9, and a plurality of regions are sandwiched between the heat exchanger 2 and the cross flow fan or the motor 3 that rotates the cross flow fan. Since the refrigerant branch flow path portions 10a and 10b are arranged, space saving is possible.
In addition, the brazing sheet is used for at least one of the plates such as the under plates 6A and 6B, the center plates 7A and 7B, and the over plates 8A and 8B, so that the refrigerant distributor 4 is integrally formed by a plate structure. The attaching process becomes easy.
Further, since two or more refrigerant distributor units 4A and 4B are provided and the number of refrigerant branch flow path portions 10a and 10b is equalized in each refrigerant distributor unit 4A and 4B, the refrigerant before flowing into the refrigerant distributor 4 Flow variation due to branching can be reduced.
Further, for each flow path of the refrigerant branch flow path portions 10a and 10b, the length of each flow path, the cross-sectional shape of each flow path, and the sum of the bending angles of each flow path are made equal, and the flow resistance of each flow path Therefore, the variation in the flow rate of the refrigerant flowing through the refrigerant branch flow passage portions 10a and 10b is reduced, and the heat exchange performance is improved.
In addition, by setting the diameter of the through hole of the inflow hole 16 to 3 mm or less, the refrigerant flowing in the gas-liquid two-phase state can be mixed uniformly, and the flow rate variation of the refrigerant flowing into the refrigerant branch flow path portions 10a and 10b can be reduced. .
Further, by providing the cutouts 14 so as not to interfere with the cross flow fan 3, it is possible to mount a higher-density indoor unit, so that space saving of the refrigerant distributor 4 can be realized.
In addition, since the refrigerant branch flow path portions 10a and 10b are configured by a structure in which a plurality of plates are stacked in the depth direction of the flow path, the configuration of the refrigerant distributor 4 can be simplified, and the low temperature of the refrigerant distributor 4 can be reduced. Cost and space saving can be realized.

  In the first embodiment, the case where the number of the refrigerant distributor units 4A and 4B is two and the number of the refrigerant branch channels 10a and 10b is four has been described. However, the number of the refrigerant distributor units 4A and 4B, The number of the refrigerant branch channels 10a and 10b is arbitrary. Moreover, although the case where the sum total of the bending angles of the refrigerant branch flow paths 10a and 10b is 315 degrees has been described, the sum of the bending angles of the refrigerant branch flow paths 10a and 10b is also arbitrary.

Furthermore, in the first embodiment, an example in which a three-layer plate structure is used has been shown. However, for example, as shown in FIG. 5, two plate layers of an over plate 8A, 8B and an under plate 6A, 6B may be used. Good.
In the configuration shown in FIG. 5, the heat transfer tube connecting portions 13a, 13b, 13c, and 13d are provided on the over plates 8A and 8B, the refrigerant branching portion 9, the refrigerant branch flow passage portions 10a and 10b, and the heat exchanger inflow The part 11, the U bend part 12, and the refrigerant gas joining part 21 are provided. For example, the overplates 8 </ b> A and 8 </ b> B can be formed by pressing.
Further, the refrigerant branching section 9, the refrigerant branch flow path sections 10a and 10b, the heat exchanger inflow section 11, the U bend section 12, and the refrigerant gas junction section 21 may be provided on the under plate 6 to form a two-layer structure. Absent.
Furthermore, a two-layer structure may be provided by providing both the over plate 8 and the under plate 6.

  Moreover, as shown in FIG. 6, you may comprise by the plate structure of three or more layers, and it becomes easy to press a part with narrow flow path widths, such as refrigerant | coolant branch flow path parts 10a and 10b in this case. This configuration is similar to that previously described for FIG.

Further, as shown in FIG. 7, the refrigerant distributor 4 may have a five-layer structure, and the refrigerant gas merging portion 21 may be provided in a different layer from the refrigerant branching portion 9 and the refrigerant branch flow passage portions 10a and 10b.
7, instead of the center plates 7A and 7B shown in FIG. 2 in the first embodiment, first center plates 71A and 71B, second center plates 72A and 72B, and third center plates 73A and 73B are provided. .
The first center plates 71A and 71B are provided with a refrigerant distribution section 9, refrigerant branch flow path sections 10a and 10b, a heat exchanger inflow section 11, and a U-bend section 12. The second center plates 72A and 72B are provided with a communication port 92 and a communication port 212. The third center plates 73A and 73B are provided with the refrigerant gas junction 21 and the communication port 93.
The under plate 6A, the center plates 71A, 72A, 73A, and the over plate 8A are superposed on each other to form the refrigerant distributor unit 4A. The under plate 6B, the center plates 71B, 72B, 73B, and the over plate 8B Are superposed on each other to form the refrigerant distributor unit 4B.
In addition, it is arbitrary in which layer the refrigerant | coolant branching part 9, the refrigerant | coolant branch flow path parts 10a and 10b, the U bend part 12, and the refrigerant gas confluence | merging part 21 are provided.

  In FIG. 7, the refrigerant that has flowed into the inflow holes 16 provided in the under plates 6A and 6B passes through the communication ports 93 and 92 provided in the third center plates 73A and 73B and the second center plates 72A and 72B. 1 The refrigerant is introduced into the refrigerant distribution section 9 provided in the center plates 71A and 71B, and is distributed to the refrigerant branch flow path sections 10a and 10b by the refrigerant distribution section 9.

The refrigerant that has passed through the flow paths of the refrigerant branch flow path portions 10 a and 10 b flows into the heat exchanger inflow portion 11.
As shown in FIG. 4, the refrigerant 19 flows from the heat exchanger inflow portion 11 provided in each of the first center plates 71A and 71B to the heat transfer tube 18a through the heat transfer tube connection portion 13a, and the heat exchanger body. Heat exchange is performed with air 23 through fins in 2 and gradually evaporates. The heat transfer tube 18a and the heat transfer tube 18b are connected at the end of the heat exchanger opposite to the refrigerant distributor units 4A and 4B, and the refrigerant 19 passes through the heat transfer tube 18b and again from the heat transfer tube connection portion 13b to the refrigerant distributor unit. It flows into 4A and 4B. The refrigerant 19 that has flowed into the refrigerant distributor units 4A and 4B again passes through the U-bend portion 12 provided in each of the first center plates 71A and 71B, flows into the heat transfer tube 18c from the heat transfer tube connection portion 13c, and is transmitted. Heat is exchanged inside the heat exchanger body 2 while passing through the heat pipe 18c.
The refrigerant 19 flows out of the heat transfer tube outlet 17 from the heat transfer tube 18d through the heat transfer tube connecting portion 13d in a single-phase state of the refrigerant gas, and passes through the communication ports 212 provided in the second center plates 72A and 72B, respectively. Then, the refrigerant gas is joined to the refrigerant gas merging portion 21 provided in the third center plates 73A and 73B. The refrigerant gas merging portion 21 merges with the refrigerant 19 that has passed through another refrigerant flow path. Thereafter, the refrigerant 19 flows out from the outflow holes 22 provided in the under plates 6 </ b> A and 6 </ b> B to piping connected to the heat exchanger body 2.

  Thus, in the modified example of the refrigerant distributor 4 shown in the first embodiment, the refrigerant gas merging portion 21 is provided in a plate layer different from the plate layer in which the refrigerant branch flow passage portions 10a and 10b are provided. Thus, the thickness of the refrigerant distributor 4 increases, but the width W of the distributor can be reduced.

  According to Embodiment 1 of the present invention, the heat exchanger main body 2 having a refrigerant flow path and the refrigerant distributor 4 for distributing and supplying the refrigerant to the predetermined flow path portion of the heat exchanger main body 2 are provided. In the heat exchanger, the refrigerant distribution part 9 for dividing the refrigerant from the refrigerant inlet 16 and the refrigerant divided by the refrigerant distribution part 9 are distributed at a predetermined flow rate to a plurality of predetermined flow path portions in the heat exchanger body 2. Center plates 7A, 7B, 71A, 71B (FIGS. 2, 6 and 7) having refrigerant branch flow path portions 10a, 10b having refrigerant throttling functions instead of capillary tubes in the prior art A plate-like distribution member comprising overplates 8A and 8B (FIG. 5) is provided as a component of the refrigerant distributor 4, and a center plate that overlaps each other and includes the plate-like distribution member A, 7B, 71A, 71B (FIGS. 2, 6 and 7) or overplates 8A, 8B (FIG. 5) and underplates 6A, 6B and center plates 72A, 72B (FIG. 7) and overplates 8A, 8B ( The refrigerant distributor 4 is constituted by a plurality of plate-like members such as FIG. 2, FIG. 6, FIG. 7) and the like, and a U vent portion 12 for communicating a predetermined portion of the flow path portion in the heat exchanger body 2 with each other. Since the communication channel comprising the plate-like distribution member is provided in the plate-like distribution member, the function of distributing the refrigerant to the predetermined flow path portion in the heat exchanger main body and the refrigerant between the predetermined portions of the flow path portion in the heat exchanger main body with a simple configuration It is possible to obtain a heat exchanger equipped with a refrigerant distributor that can accurately perform the distribution function and can realize cost reduction and space saving.

  Further, according to the first embodiment of the present invention, the center plate 7A, 7B71A, 71B (FIG. 2, FIG. FIG. 7) is a plate-like distribution member having an opening connection portion composed of a plurality of heat transfer tube connection portions 13a, 13b, 13c, 13d that communicates a predetermined flow passage portion with a predetermined flow passage portion of the heat exchanger body 2. Since the plate-like connecting member composed of the plates 8A and 8B is provided, the refrigerant distribution function and the heat exchanger main body can be achieved with a simple structure by providing the plate-like connecting member that overlaps with the plate-like distributing member and has an opening connecting portion. Equipped with a refrigerant distributor that can accurately perform the distribution function of the refrigerant to the predetermined flow path portion, and can realize cost reduction and space saving. It is possible to obtain a heat exchanger.

  Further, according to the first embodiment of the present invention, in the configuration of the preceding paragraph, the center plates 7A, 7B, 71A, 71B (one surface of which is disposed on the heat exchanger main body 2 side) (FIGS. 2, 6, and 6) 7) or a plate-like adherent member comprising underplates 6A and 6B which are deposited on the other surface of the plate-like distribution member comprising overplates 8A and 8B (FIG. 5) and polymerized, and the plate-like adherent member Provided with a refrigerant inlet comprising an inflow hole 16 corresponding to a refrigerant inlet comprising the refrigerant distribution portion 9 of the plate-like distribution member. By providing it, the distribution function of the refrigerant and the distribution function of the refrigerant to the predetermined flow path portion of the heat exchanger main body can be accurately performed with a simple configuration, and cost reduction and space saving can be realized. Both can be obtained a heat exchanger provided with the refrigerant distributor to properly perform the introduction of the refrigerant to the refrigerant distributor.

  Further, according to Embodiment 1 of the present invention, in any one of the configurations of the preceding three items, the refrigerant distributor may be the center plate 7A, 7B, 71A, 71B (FIGS. 2, 6, 6) or over. A plurality of plate-like members that are superposed on each other including a plate-like distribution member composed of plates 8A and 8B (FIG. 5), and a brazing material is applied to the surface of at least one of the plurality of plate-like members. A plurality of plate-like members that are superposed on each other, including a plate-like distribution member that constitutes the refrigerant distributor, using a sheet member made of a brazing plate, are joined together by brazing of the brazing plate. Therefore, the refrigerant distribution function and the refrigerant distribution function to the predetermined flow path of the heat exchanger body can be accurately achieved with a simple configuration. Can, together with low cost can be realized and space saving, it is possible to obtain a heat exchanger provided with the refrigerant distributor can be easily manufactured.

  Further, according to Embodiment 1 of the present invention, in any one of the configurations of the preceding four items, the refrigerant branching portion 9 for branching the refrigerant from the refrigerant inlet 16 and the refrigerant branched by the refrigerant branching portion 9 are First center plates 7A and 71A (FIGS. 2, 6, and 7) having refrigerant branch flow path portions 10a and 10b for supplying a predetermined flow rate to predetermined flow path portions at a plurality of locations in the heat exchanger body 2 or The first plate-like distribution member composed of the first overplate 8A (FIG. 5), the refrigerant distribution part 9 for dividing the refrigerant from the refrigerant inlet 16, and the refrigerant divided by the refrigerant distribution part 9 perform the heat exchange. Second center plates 7B and 71B (FIGS. 2, 6, and 7) having refrigerant branch flow path portions 10a and 10b for supplying a predetermined flow rate to predetermined flow path portions at a plurality of locations in the vessel body 2. A second plate-like distribution member made of an overplate 8B (FIG. 5), and extending the first plate-like distribution member and the second plate-like distribution member on the same plane, The first plate-like distribution member and the second plate-like distribution member are arranged so that the extending direction of one plate-like distribution member and the extending direction of the second plate-like distribution member have a predetermined angle. Since the plate-like distribution member is constituted by the first plate-like distribution member and the second plate-like distribution member, the first plate-like distribution member and the second plate-like distribution member are appropriately arranged. By disposing, the refrigerant distribution function and the refrigerant distribution function to the predetermined flow path portion of the heat exchanger main body can be accurately performed with a simple configuration, and the refrigerant can realize cost reduction and space saving more appropriately. Min Vessel can be obtained a heat exchanger provided with the.

  In addition, according to the first embodiment of the present invention, the heat exchanger main body disposed along the axis of the crossflow fan 3 for ventilating the heat exchanger main body 2 in any one of the configurations of the preceding five items A plate-like distribution member made up of the center plates 7A, 7B, 71A, 71B (FIGS. 2, 6 and 7) or overplates 8A and 8B (FIG. 5) is disposed along the end face 2a. Since the edge portion FG of the plate-like distribution member faces the circumferential surface 3a of the cross flow fan or the motor 3 that rotates the cross flow fan, the edge portion of the plate-like distribution member has a cross flow fan or cross. By properly disposing the flow fan so as to face the motor circumferential surface, the refrigerant distribution function and the predetermined heat exchanger body can be determined with a simple configuration. Distribution function of refrigerant to the road section can accurately perform, it is possible to obtain a heat exchanger provided with the refrigerant distributor that can more appropriately realize a cost reduction and space saving.

  Further, according to Embodiment 1 of the present invention, in the configuration of the preceding paragraph, the refrigerant distributor 4 is replaced with a center plate 7A, 7B, 71A, 71B (FIGS. 2, 6 and 7) or an overplate 8A, 8B ( Of the motor 3 for rotating the cross flow fan or the cross flow fan in at least one of the plurality of plate members. Since the notch 14 is provided in the portion facing the peripheral surface 3a, the plate-like member is appropriately arranged so that the edge portion thereof faces the cross-flow fan peripheral surface, and the cross-flow fan or cross-flow of the plate-like member is arranged. By providing a notch in the part facing the motor peripheral surface that rotates the fan, the refrigerant can be separated with a simple structure. A heat exchanger having a refrigerant distributor that can accurately perform the function and the refrigerant distribution function to the predetermined flow path portion of the heat exchanger main body, and can further appropriately realize cost reduction and space saving. .

  Further, according to the first embodiment of the present invention, in the configuration of any one of the preceding seven items, since the diameter of the refrigerant inflow hole 16 is 3 mm or less, the refrigerant distribution function and the heat exchanger body can be achieved with a simple configuration. The refrigerant distribution function to the predetermined flow path part can be accurately performed, cost reduction and space saving can be realized, and the refrigerant flowing in the gas-liquid two-phase state can be mixed uniformly, and the refrigerant flowing to each branch flow path It is possible to obtain a heat exchanger including a refrigerant distributor that can reduce the flow rate variation.

  Further, according to the first embodiment of the present invention, the refrigerant distributor 4 is arranged in the center plate 7A, 7B, 71A, 71B (FIG. 2, FIG. 6, FIG. 7) or over in the configuration according to any one of the preceding eight items. A plurality of plate-like members that are superposed on each other, including a plate-like distribution member comprising plates 8A and 8B (FIG. 5), and the refrigerant branch flow path portions 10a and 10b are formed of the plate-like distribution member and the under plate 6A, The plate-like distribution member is formed by joining the adjacent plate-like member such as the plate-like adherence member, which is provided on the overlapping surface of the plate-like adhering member such as the plate-like adhering member made of 6B. The dimension of the refrigerant branch flow path portions 10a and 10b in the depth direction of the refrigerant is restricted, and the depth of the refrigerant branch flow path portion is set. Therefore, by restricting the depth dimension of the flow path of the refrigerant branch flow path portion by joining the plate-shaped distribution member and the plate-shaped member to be superposed, the refrigerant distribution function and the predetermined flow path portion of the heat exchanger main body can be achieved with a simple configuration. Thus, it is possible to obtain a heat exchanger equipped with a refrigerant distributor that can accurately perform the refrigerant distribution function and can realize cost reduction and space saving more appropriately.

  Further, according to Embodiment 1 of the present invention, in any one of the configurations of the preceding nine items, center plates 7A, 7B, 71A, 71B having refrigerant branch flow path portions 10a, 10b (FIGS. 2, 6, and 6), respectively. 7) or a refrigerant distributor 4 comprising a plurality of refrigerant distributor units 4A, 4B provided with plate-like distribution members comprising overplates 8A, 8B (FIG. 5), and each refrigerant distributor unit 4A, 4B. Since the number of the refrigerant branch flow path portions 10a and 10b in each of the refrigerant distributor units is made equal, the number of refrigerant branch flow path portions in each refrigerant distributor unit is made equal to reduce the flow rate variation when branching the refrigerant, and the refrigerant can be made by a simple configuration. Refrigerant distribution function that can accurately perform the distribution function of the refrigerant and the distribution function of the refrigerant to the predetermined flow path portion of the heat exchanger body, and can further appropriately realize cost reduction and space saving It is possible to obtain a heat exchanger equipped.

  Further, according to the first embodiment of the present invention, in the configuration of any one of the preceding ten items, a plurality of the refrigerant branch flow passage portions 10a and 10b are provided, and each flow in the plurality of refrigerant branch flow passage portions 10a and 10b is provided. Since the length of the path, the cross-sectional shape of each flow path, and the sum of the bending angles of each flow path are made equal, it is possible to improve the heat exchange performance by reducing the flow rate variation when the refrigerant is branched, and with a simple configuration A heat exchanger having a refrigerant distributor that can accurately perform a refrigerant distribution function and a refrigerant distribution function to a predetermined flow path portion of the heat exchanger main body, and can further appropriately realize cost reduction and space saving. be able to.

  Further, according to Embodiment 1 of the present invention, in any one of the constitutions of the previous 11 items, the refrigerant branch flow path portions 10a and 10b are distributed and supplied to the heat exchanger main body 2 to be supplied from the heat exchanger main body 2. A plate comprising the center plates 7A and 7B (FIGS. 2 and 6) or the overplates 8A and 8B (FIG. 5) constituting the refrigerant distributor as a refrigerant gas junction 21 for collecting or distributing the flowing refrigerant gas. By providing the refrigerant gas merging portion on the plate-like distribution member, the refrigerant distribution function and the refrigerant distribution function to the predetermined flow path portion in the heat exchanger body can be accurately performed by providing the refrigerant gas confluence portion on the plate-like distribution member. Thus, it is possible to obtain a heat exchanger including a refrigerant distributor that can realize cost reduction and space saving more appropriately.

  Further, according to the first embodiment of the present invention, in any one of the constitutions of the preceding twelve items excluding the preceding item, the refrigerant distributor is superposed on each other including a plate-like distribution member comprising center plates 71A and 71B (FIG. 7). The plate-like confluence comprising the third center plates 73A and 73B (FIG. 7) different from the plate-like distribution member is formed by a plurality of plate-like members and the refrigerant gas confluence portion for collecting the refrigerant gas. Since it is provided on a plate-like member such as a member, the refrigerant gas merging portion is provided on a plate-like distribution member that is different from the plate-like distribution member. It is possible to obtain a heat exchanger equipped with a refrigerant distributor that can accurately perform a refrigerant distribution function to a portion, and can further appropriately realize cost reduction and space saving. Kill.

  Further, according to the embodiment of the present invention, in the configuration of the preceding paragraph, the refrigerant branching portion 9 for dividing the refrigerant from the refrigerant inlet 16 and the refrigerant diverted by the refrigerant branching portion 9 in the heat exchanger main body 2 A plate-like distribution member comprising first center plates 71A, 71B (FIG. 7) having refrigerant branch flow passage portions 10a, 10b having a refrigerant throttling function for supplying a predetermined flow rate to a plurality of predetermined flow passage portions; Overplates 8A and 8B having a plurality of opening connection portions arranged in a manner overlapping with a plate-like distribution member and communicating a predetermined flow path portion of the plate-shaped distribution member with a predetermined flow path portion of the heat exchanger body 2 Plate-shaped connecting members and second center plates 72A and 72B superposed on the other surface of the plate-shaped distribution member disposed on the heat exchanger main body side. 7) and a plate-like connecting member, a plate-like distributing member, and a plate-like communicating member that are superposed on the other surface of the plate-like communicating member disposed on the heat exchanger body side. A plate-like joining member comprising third center plates 73A and 73B (FIG. 7) provided with joining portions 21 communicating with the refrigerant outlets from a plurality of locations of the heat exchanger main body 2 through the refrigerant communication ports provided in And a plate-like adherent member comprising underplates 6A and 6B superposed on the other face of the plate-like joining member disposed on the heat exchanger main body side, and the plate-like adherent member includes the plate-like adherent member. A refrigerant inlet comprising an inflow hole 16 communicating with the refrigerant inlet of the plate-like distribution member through the plate-like junction member and the refrigerant communication port is provided, and Since the refrigerant outlet comprising the outflow hole 22 communicating with the joining portion 21 of the gate-like joining member is provided, the plate-like joining member having the joining portion in addition to the plate-like distribution member, the plate-like connecting member, and the plate-like attaching member By configuring the refrigerant distributor, it is possible to accurately perform the refrigerant distribution function and the refrigerant distribution function to the predetermined flow path portion of the heat exchanger main body with a simple configuration, and further appropriately reduce cost and space saving. A heat exchanger including a refrigerant distributor that can be realized can be obtained.

Embodiment 2. FIG.
A second embodiment of the present invention will be described with reference to FIGS. FIG. 8 is a side view showing the configuration of the refrigerant distributor in the second embodiment. FIG. 9 is a perspective view illustrating an overall configuration for explaining a state when the heat exchanger provided with the refrigerant distributor in the second embodiment is installed in the indoor unit 1 for air conditioning.
In the second embodiment, the configuration other than the specific configuration described here has the same configuration contents as the configuration in the first embodiment described above, and exhibits the same operation. In the drawings, the same reference numerals indicate the same or corresponding parts.

In the second embodiment, the refrigerant gas merging portion 21 is not provided in the refrigerant distributor 4, and the refrigerant gas merging portion 21 is installed outside the refrigerant distributor 4.
That is, in the first embodiment, plate-like members such as a plate-like distribution member consisting of the center plates 7A and 7B, a plate-like connecting member consisting of the over plates 8A and 8B, and a plate-like adherent member consisting of the under plates 6A and 6B. The refrigerant distributor 4 including the refrigerant distributor units 4A and 4B is configured, and the refrigerant gas merging portion 21 is provided in the center plates 7A and 7B and the like. In the second embodiment, the refrigerant distributor unit 4A and 4B is configured by a plate-like member. A refrigerant gas junction 21 is installed outside the refrigerant distributor 4.

In the second embodiment, as shown in FIG. 9, for example, the refrigerant gas joining portion 21 is arranged along the extending direction of the refrigerant distributor 4 extending in parallel with the end surface 2 a of the heat exchanger body 2. It can be configured with a structure in which the branch pipe 21b is provided in the pipe 21a provided.
The branch pipe 21b provided in the pipe 21a communicates with the heat transfer pipe outlet 17, and the refrigerant from the heat transfer pipe 18a of the heat exchanger body 2 passes through the heat transfer pipe outlet 17 and is collected by the pipe 21a through the branch pipe 21b.

Next, the operation of the refrigerant will be described. As in the first embodiment, the refrigerant 19 exchanges heat with the air 23 and flows out of the refrigerant distributor 4 through the heat transfer tube outlet 17 in a single-phase state of the refrigerant gas. Thereafter, the refrigerant 19 that has flowed out of the refrigerant distributor 4 joins at the refrigerant gas junction 21. Normally, the temperature of the refrigerant 19 in the refrigerant gas single-phase state is higher than the temperature of the refrigerant 19 in the gas-liquid two-phase state.
Here, in the second embodiment, the refrigerant gas merging portion 21 is provided separately from the refrigerant distributor 4, so that the high-temperature refrigerant 19 that has become the refrigerant gas is directed to the low-temperature refrigerant 19 that is in a gas-liquid two-phase state. , The amount of heat transfer decreases. Therefore, the amount of heat exchange between the high-temperature refrigerant 19 and the low-temperature refrigerant 19 is reduced, and the amount of heat exchange between the refrigerant 19 and the air 23 is increased, so that the performance of the heat exchanger is improved.

In FIG. 9, the refrigerant gas merging portion 21 is shown with a structure in which a branch pipe is provided in the pipe. However, any structure can be used as long as the refrigerant gas can be collected or branched.
In the second embodiment, the refrigerant gas merging portion 21 is arranged on the side surface of the refrigerant distributor 4. However, it is obvious that the same effect can be obtained even if arranged on the outer periphery of the refrigerant distributor 4.

  According to the second embodiment of the present invention, in the configuration of the first embodiment, the plate-like distribution member composed of the center plates 7A, 7B constituting the refrigerant distributor 4 composed of the refrigerant distributor units 4A, 4B, and the overload. A branch pipe 21b that is configured separately from the plate-like connecting member made of the plates 8A and 8B and the plate-like member such as the plate-like adherent member made of the under plates 6A and 6B, and is arranged outside the refrigerant distributor 4. Since the refrigerant gas merging portion 21 comprising the pipe 21a provided with the refrigerant gas is provided, the heat exchange performance is improved by providing the refrigerant gas merging portion separately from the plate-like member constituting the refrigerant distributor, and the refrigerant has a simple structure. Distribution function and refrigerant distribution function to the specified flow path part of the heat exchanger body can be performed accurately, reducing costs and saving space It is possible now, heat exchange performance can be improved, it is possible to obtain a heat exchanger provided with the refrigerant distributor.

Embodiment 3 FIG.
A third embodiment of the present invention will be described with reference to FIG. FIG. 10 is a side view showing the configuration of the refrigerant distributor 4 in the third embodiment, and is a diagram for explaining the flow path configuration of the refrigerant branch flow path section.
In the third embodiment, the configuration other than the specific configuration described here has the same configuration contents as the configurations in the first and second embodiments described above and exhibits the same operation. It is. In the drawings, the same reference numerals indicate the same or corresponding parts.

In the third embodiment, this corresponds to the case where there is a wind speed distribution of the air 23 flowing into the heat exchanger main body 2, and here, the air 23a passing through the heat exchanger main body 2 located near the cross flow fan 3 The case where the wind speed is high is shown.
In the third embodiment, the refrigerant branch flow path portions 10a, 10c, and 10b are provided, and the refrigerant is supplied to predetermined portions of the heat transfer tubes 18a, 18b, 18c, and 18d that exchange heat with the air 23a having a high wind speed. The flow path width of the refrigerant branch flow path portion 10c is larger than the flow path widths of the other refrigerant branch flow path widths 10a.
For this reason, the flow resistance of the refrigerant branch channel portion 10c is reduced, and the flow rate of the refrigerant flowing through the refrigerant branch channel portion 10c is increased. Therefore, the heat transfer tubes 18a, 18b, 18c corresponding to the portion through which the air 23a having a high wind speed passes. , 18d, a large amount of refrigerant can be caused to flow through the refrigerant branch channel portion 10c, and heat exchange performance is improved.

  Here, the flow resistance is reduced by increasing the flow path width, but the same effect can be obtained even when the flow resistance is reduced by increasing the cross-sectional shape such as the flow path height. Is clear.

  According to Embodiment 3 of the present invention, in the configuration in Embodiment 1 or Embodiment 2, a plurality of refrigerant branch flow passage portions 10a, 10c and 10b are provided, and the plurality of refrigerant branch flow passage portions 10a, 10b are provided. , 10c, the cross-sectional shape such as the channel width and the channel height of each channel is changed according to the velocity distribution of the heat exchange target airs 23 and 23a flowing into the heat exchanger body 2, and the plurality of refrigerant branches Since the flow resistance of each flow path in the flow path portions 10a, 10b, 10c is changed according to the velocity distribution of the heat exchange target air 23, 23a flowing into the heat exchanger body 2, the flow resistance in the plurality of refrigerant branch flow path portions By changing the flow resistance of each flow path according to the velocity distribution of the heat exchange target air, the refrigerant distribution function and the refrigerant distribution function to the predetermined flow path portion of the heat exchanger body are accurately achieved with a simple configuration. Can, together with low cost can be realized and space saving, the heat exchanging performance can be improved, it is possible to obtain a heat exchanger provided with the refrigerant distributor.

Embodiment 4 FIG.
A fourth embodiment of the present invention will be described with reference to FIG. FIG. 11 is a side view showing the configuration of the refrigerant distributor 4 in the fourth embodiment, and is a view for explaining the flow path configuration of the refrigerant branch flow path section.
In the fourth embodiment, the configuration other than the specific configuration described here has the same configuration contents as those in the first to third embodiments described above, and has the same operation. Is. In the drawings, the same reference numerals indicate the same or corresponding parts.

As in the third embodiment, the fourth embodiment corresponds to the case where there is a wind speed distribution of the air 23 flowing into the heat exchanger 2, and the air 23a that passes through the heat exchanger located near the cross flow fan. The case where the wind speed is high is shown.
In the fourth embodiment, the refrigerant branch flow path portions 10a, 10d, and 10b are provided, but the refrigerant is supplied to predetermined portions of the heat transfer tubes 18a, 18b, 18c, and 18d that exchange heat with the air 23a having a high wind speed. The sum total of the bending angles of the refrigerant branch flow path portion 10d is smaller than the sum of the bending angles of the other refrigerant branch flow paths 10a. For example, in FIG. 9, the sum of the bending angles of the refrigerant branch flow path portion 10d is 45 + 90 degrees = 135 degrees, but the total of the bending angles of the other refrigerant branch flow path portions 10 is 315 degrees.
For this reason, the flow resistance of the refrigerant branch passage portion 10d is reduced, and the flow rate of the refrigerant flowing through the refrigerant branch passage portion 10d is increased. Therefore, the heat transfer tubes 18a, 18b, and 18c corresponding to the portion through which the air 23a having a high wind speed passes. , 18d, a large amount of refrigerant can be caused to flow through the refrigerant branch flow path portion 10d, and heat exchange performance is improved.

Here, the sum of the bending angles of the refrigerant branch flow passage 10d is made smaller than the sum of the bending angles of the other refrigerant branch flow passages 10a to adjust the flow resistance of the refrigerant branch flow passages 10a, 10b, 10d. The flow resistance of the refrigerant branch flow path portions 10a, 10b, and 10d is described in combination with the increase and decrease of the flow resistance caused by the change in the cross-sectional shape of the refrigerant branch flow path portion 10c described in the third embodiment. May be adjusted.
In other words, the sum of the bending angles of the refrigerant branch flow path portion 10d is made smaller than the sum of the bending angles of the other refrigerant branch flow passage portions 10a and 10b, and the flow paths of the refrigerant branch flow passage portions 10a, 10b and 10d. The flow resistance can be adjusted by changing the cross-sectional shape of the refrigerant to adjust the flow resistance of the refrigerant branch flow path portions 10a, 10b, and 10d.

  According to Embodiment 4 of the present invention, in the configuration of Embodiment 1 or Embodiment 2, a plurality of refrigerant branch flow passage portions 10a, 10d and 10b are provided, and the plurality of refrigerant branch flow passage portions 10a, 10b are provided. , 10d is changed according to the velocity distribution flowing into the heat exchanger body 2, and the flow resistance of each flow path in the plurality of refrigerant branch flow path portions 10a, 10b, 10d is changed. Since the heat exchange target air 23, 23a flowing into the heat exchanger main body 2 is changed according to the velocity distribution of the heat exchange target air 23, the flow resistance of each flow path in the plurality of refrigerant branch flow paths is determined according to the velocity distribution of the heat exchange target air. By changing the function, the distribution function of the refrigerant and the distribution function of the refrigerant to the predetermined flow path part of the heat exchanger body can be accurately performed with a simple configuration, thereby realizing cost reduction and space saving. Together, the heat exchanging performance can be improved, it is possible to obtain a heat exchanger provided with the refrigerant distributor.

Embodiment 5. FIG.
A fifth embodiment of the present invention will be described with reference to FIG. FIG. 12 is a side view showing the configuration of the refrigerant distributor in the fifth embodiment, and is a view for explaining the flow path configuration of the refrigerant branch flow path section.
In the fifth embodiment, the configuration other than the specific configuration described here has the same configuration contents as those in the first to fourth embodiments described above, and exhibits the same operation. Is. In the drawings, the same reference numerals indicate the same or corresponding parts.

The fifth embodiment corresponds to the case where there is a wind speed distribution of the air 23 flowing into the heat exchanger, as in the third and fourth embodiments. Here, the heat located near the cross flow fan is used. The case where the wind speed of the air 23a which passes an exchanger is large is shown.
In the fifth embodiment, the refrigerant branch flow path portions 10a, 10e, and 10b are provided. However, with respect to the refrigerant branch flow path portion 10e, the length of each flow path and the total bending angle of each flow path are other than It is smaller than the refrigerant branch flow path portion 10.
For this reason, the flow resistance of the refrigerant branch flow path portion 10e is reduced, and the flow rate of the refrigerant flowing through the refrigerant branch flow path portion 10e is increased. Therefore, a large amount of refrigerant can flow through the portion through which the air 23a having a high wind speed passes. , Heat exchange performance is improved.

Here, with respect to the refrigerant branch flow path portion 10d, the length of each flow path and the sum of the bending angles of the respective flow paths are made smaller than those of the other refrigerant branch flow paths 10a and 10b, and the refrigerant branch flow path portion 10a. , 10b, 10e for adjusting the flow resistance, the increase and decrease of the flow resistance due to the change in the cross-sectional shape of the refrigerant branch flow path portion 10c described in the third embodiment is used in combination with this. You may make it adjust the flow resistance of the part 10a, 10b, 10e.
That is, with respect to the refrigerant branch flow path portion 10e, the total length of each flow path and the bending angle of each flow path is made smaller than those of the other refrigerant branch flow path portions 10a, and the refrigerant branch flow path portions 10a and 10b. , 10e, the flow resistance can be increased or decreased by changing the cross-sectional shape of the flow path, and the flow resistance of the refrigerant branch flow path portions 10a, 10e can be adjusted.

Here, an example is shown in which both the flow path length and the total bending angle of the refrigerant branch flow path portion 10e are simultaneously reduced, but the same effect can be obtained even when only the flow path length is reduced. It is clear to have.
That is, only the flow path length of the refrigerant branch flow path portion 10e is made smaller than that of the other refrigerant branch flow paths 10a to adjust the flow resistance of the refrigerant branch flow path portions 10a, 10b, and 10e. Good.
And about the refrigerant | coolant branch flow path part 10e, while making the length of each flow path smaller than the other refrigerant | coolant branch flow path part 10a, the cross-sectional shape of the flow path of the refrigerant | coolant branch flow path parts 10a, 10b, 10e is changed. Thus, the flow resistance can be increased or decreased to adjust the flow resistance of the refrigerant branch flow path portions 10a, 10b, and 10e.

  In the fifth embodiment, at least one of the length of each flow path of the refrigerant branch flow path portions 10a, 10b, and 10e, the cross-sectional shape of each flow path, and the total bending angle of each flow path is subjected to heat exchange. By changing according to the speed distribution of the heat exchange target airs 23 and 23a flowing into the heat exchanger body 2, the refrigerant branching flow is matched to the speed distribution of the heat exchange target airs 23 and 23a flowing into the heat exchanger main body 2 By adjusting at least one of the length of each flow path of the path portions 10a, 10b, and 10e, the cross-sectional shape of each flow path, and the total bending angle of each flow path, the refrigerant branch flow path portions 10a, 10b, Since the flow resistance of 10e is adjusted, the flow resistance of each refrigerant branch channel part can be controlled, and the heat transfer performance of the heat exchanger can be improved.

  According to Embodiment 5 of the present invention, in the configuration in Embodiment 1 or Embodiment 2, a plurality of refrigerant branch flow passage portions 10a, 10e and 10b are provided, and the plurality of refrigerant branch flow passage portions 10a, 10b are provided. , 10e, the flow path length of each flow path is changed according to the velocity distribution of the heat exchange target air 23, 23a flowing into the heat exchanger body 2, and each of the plurality of refrigerant branch flow path portions 10a, 10d is changed. Since the flow resistance of the flow path is changed according to the velocity distribution of the heat exchange target airs 23 and 23a flowing into the heat exchanger body 2, the flow resistance of each flow path in the plurality of refrigerant branch flow path portions is subject to heat exchange. By changing according to the velocity distribution of air, the distribution function of the refrigerant and the distribution function of the refrigerant to the predetermined flow path part of the heat exchanger body can be accurately performed with a simple configuration, thereby reducing costs and saving space. Together can be realized, the heat exchanging performance can be improved, it is possible to obtain a heat exchanger provided with the refrigerant distributor.

  Further, according to Embodiment 5 of the present invention, in the configuration in Embodiment 1 or Embodiment 2, a plurality of refrigerant branch flow passage portions 10a, 10e and 10b are provided, and the plurality of refrigerant branch flow passage portions 10a. , 10b, and 10e, the total length of the flow paths and the sum of the bending angles are changed according to the velocity distribution of the heat exchange target airs 23 and 23a flowing into the heat exchanger body 2, and the plurality of refrigerant branch flows Since the flow resistance of each flow path in the path portions 10a, 10b, 10e is changed according to the velocity distribution of the heat exchange target air 23, 23a flowing into the heat exchanger main body 2, each flow rate in each of the plurality of refrigerant branch flow path portions is changed. By changing the flow resistance of the flow path according to the velocity distribution of the heat exchange target air, the refrigerant distribution function and the refrigerant distribution function to the predetermined flow path portion of the heat exchanger body can be accurately achieved with a simple configuration. Execution can, it is possible to realize low cost and space saving, the heat exchanging performance can be improved, it is possible to obtain a heat exchanger provided with the refrigerant distributor.

  Furthermore, according to Embodiment 5 of the present invention, in the configuration in Embodiment 1 or Embodiment 2, a plurality of refrigerant branch flow passage portions 10a, 10e and 10b are provided, and the plurality of refrigerant branch flow passage portions 10a. , 10b, 10e at least one of the length of each flow path, the cross-sectional shape of each flow path, and the total bending angle of each flow path, the heat exchange target air 23, 23a flowing into the heat exchanger body 2 The flow resistance of each flow path in the plurality of refrigerant branch flow path portions 10a and 10e is changed according to the speed distribution of the heat exchange target air 23 and 23a flowing into the heat exchanger body 2. Therefore, by changing the flow resistance of each flow path in the plurality of refrigerant branch flow paths according to the velocity distribution of the heat exchange target air, the refrigerant distribution function and heat exchange can be achieved with a simple configuration. To obtain a heat exchanger equipped with a refrigerant distributor that can accurately perform a refrigerant distribution function to a predetermined flow path portion of the vessel body, achieve cost reduction and space saving, and improve heat exchange performance Can do.

Embodiment 6 FIG.
A sixth embodiment of the present invention will be described with reference to FIG. FIG. 13 is a side view showing the configuration of the refrigerant distributor in the sixth embodiment.
In the sixth embodiment, the configuration other than the specific configuration described here has the same configuration contents as those in the first to fifth embodiments described above, and exhibits the same operation. Is. In the drawings, the same reference numerals indicate the same or corresponding parts.

In the sixth embodiment, a flat tube 25 is used instead of a circular tube for the heat transfer tubes 18a, 18b, 18c, 18d of the heat exchanger body 2. The flat tube 25 is provided with a plurality of fine holes in the tube.
When the refrigerant distributor 4 is attached to the heat exchanger, the operation of the refrigerant flowing through the refrigerant distributor 4 is the same as in the second embodiment. However, when the refrigerant passes through the flat tube 25, it flows in a plurality of fine holes provided in the tube. In the flat tube 25, the surface area in the tube is increased due to the plurality of fine holes provided in the tube, so that the heat transfer coefficient in the tube can be improved. Further, by flattening the outer shape of the tube, the flow resistance when air passes through the fins is reduced, so that the input of the cross flow fan can be reduced.
When a heat exchanger using the flat tube 25 is manufactured, for example, the fin and the flat tube of the heat exchanger main body 2 are brazed by a continuous heat treatment furnace or the like. The brazing of the three layers of the plates 6A and 6B, the center plates 7A and 7B, and the over plates 8A and 8B, and the brazing of the refrigerant distributor 4 and the flat tube 25 can be performed at the same time, thereby reducing the manufacturing cost. .
In addition, although the flat tube was shown here as a heat exchanger tube, even if it is an elliptical tube or a thin tube (for example, 3 mm or less in internal diameter), it has the same effect.

  According to Embodiment 6 of the present invention, in any configuration from Embodiment 1 to Embodiment 5, the heat transfer tubes 18a and 18b of the heat exchanger main body 2 to which the refrigerant is supplied from the refrigerant distributor 4 are provided. , 18c, 18d (see FIGS. 3 and 4, etc.), a non-circular tube such as a flat tube 25 or an elliptic tube (not shown) having pores inside is used. Obtaining a heat exchanger equipped with a refrigerant distributor that can accurately perform the refrigerant distribution function to the predetermined flow path portion of the heat exchanger main body, realize cost reduction and space saving, and reduce manufacturing costs. be able to.

  According to Embodiment 6 of the present invention, in any configuration from Embodiment 1 to Embodiment 5, the heat transfer tube 18a of the heat exchanger body 2 to which the refrigerant is supplied from the refrigerant distributor 4 is provided. , 18b, 18c, 18d (refer to FIGS. 3, 4 and the like), a narrow tube having an inner diameter of 3 mm or less is used, so that the refrigerant distribution function and the circulation of the refrigerant to a predetermined flow path portion of the heat exchanger body can be achieved with a simple configuration. It is possible to obtain a heat exchanger equipped with a refrigerant distributor that can accurately perform its functions, realize cost reduction and space saving, and reduce manufacturing costs.

The perspective view which shows the whole structure for demonstrating a mode when the heat exchanger provided with the refrigerant distributor in Embodiment 1 by this invention is installed in the indoor unit 1 for an air conditioning. 1 is an exploded perspective view showing a configuration of a refrigerant distributor according to Embodiment 1 of the present invention. The side view for demonstrating operation | movement of the refrigerant | coolant which flows through the refrigerant distributor in Embodiment 1 by this invention. The expanded sectional view along the IV-IV line of the refrigerant distributor in Embodiment 1 by this invention. The disassembled perspective view which shows the structure of the refrigerant distributor for demonstrating the modification in Embodiment 1 by this invention. The disassembled perspective view which shows the structure of the refrigerant distributor for demonstrating the other modification in Embodiment 1 by this invention. The disassembled perspective view which shows the structure of the refrigerant distributor for demonstrating the further another modification in Embodiment 1 by this invention. The side view which shows the structure of the refrigerant distributor in Embodiment 2 by this invention. The perspective view which shows the whole structure for demonstrating a mode when the heat exchanger provided with the refrigerant distributor in Embodiment 2 by this invention is installed in the indoor unit 1 for an air conditioning. The side view which shows the structure of the refrigerant distributor in Embodiment 3 by this invention. The side view which shows the structure of the refrigerant distributor in Embodiment 4 by this invention. The side view which shows the structure of the refrigerant distributor in Embodiment 5 by this invention. The side view which shows the structure of the refrigerant distributor in Embodiment 6 by this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Air conditioning indoor unit, 2 Heat exchanger main body, 3 Cross flow fan, 4 Refrigerant distributor, 4A, 4B Refrigerant distributor unit, 6A, 6B under plate, 7A, 7B Center plate, 8A, 8B over plate, 9 Refrigerant Dividing part, 10a, 10b Refrigerant branch channel part, 11 Heat exchanger inflow part, 12 U bend part, 13a, 13b Heat transfer pipe connection part, 14 Notch, 16 Inlet hole, 17 Heat transfer pipe outlet, 18a, 18b Heat transfer pipe , 19 Refrigerant, 21 Refrigerant gas collecting part, 22 Outflow hole, 23 Heat exchange target air.

Claims (19)

  A heat exchanger comprising: a heat exchanger body having a refrigerant flow path; and a refrigerant distributor that distributes and supplies the refrigerant to a plurality of predetermined flow path portions in the heat exchanger body. And a refrigerant branch flow passage portion having a refrigerant throttling function for supplying the refrigerant diverted by the refrigerant flow division portion to a plurality of predetermined flow passage portions in the heat exchanger main body at a predetermined flow rate. A heat exchanger characterized in that a plate-like distribution member is provided, and the refrigerant distributor is constituted by a plurality of plate-like members that are superposed on each other including the plate-like distribution member.   2. The heat exchanger according to claim 1, wherein a communication flow path is provided in the plate-like distribution member for communicating predetermined portions of the flow path portion in the heat exchanger main body with each other.   A plate-like connecting member having a plurality of opening connecting portions arranged to overlap with the plate-like distribution member and communicating a predetermined flow path portion of the plate-like distribution member to a predetermined flow path portion of the heat exchanger main body is provided. The heat exchanger according to claim 1 or 2, characterized by the above.   A plate-like adherence member superposed on the other surface of the plate-like distribution member disposed on the heat exchanger main body side, the plate-like adherence member having a refrigerant inlet of the plate-like distribution member; The heat exchanger according to any one of claims 1 to 3, wherein a corresponding refrigerant inlet is provided.   The refrigerant distributor is composed of a plurality of plate-like members that are superposed on each other including the plate-like distribution member, and at least one of the plurality of plate-like members uses a sheet member having a brazing material attached to the surface thereof The heat exchanger according to any one of claims 1 to 4, wherein the heat exchanger is characterized.   A refrigerant branching portion for diverting the refrigerant from the refrigerant inlet, and a refrigerant branch passage portion for supplying the refrigerant diverted by the refrigerant branching portion to predetermined passage portions at a plurality of locations in the heat exchanger main body at a predetermined flow rate. A first plate-like distribution member having a refrigerant, a refrigerant distribution portion for dividing the refrigerant from the refrigerant inlet, and the refrigerant divided by the refrigerant distribution portion to a plurality of predetermined flow path portions in the heat exchanger main body at a predetermined flow rate. A second plate-like distribution member having a refrigerant branch channel for supplying, extending the first plate-like distribution member and the second plate-like distribution member in the same plane, and The first plate-shaped distribution member and the second plate-shaped segment are arranged such that the extending direction of the first plate-shaped distribution member and the extending direction of the second plate-shaped distribution member have a predetermined angle. A heat exchanger according to any one of claims 1 to 5, characterized in that disposed between members.   The plate-like distribution member is arranged along the end surface of the heat exchanger main body arranged along the axis of the cross flow fan for ventilating the heat exchanger main body, and the edge portion of the plate-like distribution member The heat exchanger according to any one of claims 1 to 6, wherein the heat exchanger is opposed to a circumferential surface of the crossflow fan or a motor that rotates the crossflow fan.   The refrigerant distributor is constituted by a plurality of plate-like members that are superposed on each other including the plate-like distribution member, and the circumferential surface of the cross-flow fan or the cross-flow fan in at least one of the plurality of plate-like members is rotated. The heat exchanger according to claim 7, wherein a notch is provided in a portion facing the motor to be driven.   The heat exchanger according to any one of claims 1 to 8, wherein a diameter of the refrigerant inflow hole is 3 mm or less.   The refrigerant distributor is constituted by a plurality of plate-like members that are superposed on each other including the plate-like distribution member, and the refrigerant branch channel portion is superposed on the plate-like member that is superposed adjacent to the plate-like distribution member. The size of the flow path of the refrigerant branch flow path portion in the plate-like distribution member is regulated by joining the adjacent plate-shaped members provided on the surface, and the flow path of the refrigerant branch flow path portion The heat exchanger according to claim 3, wherein the depth is set.   A refrigerant distributor comprising a plurality of refrigerant distributor units each provided with a plate-like distribution member having a refrigerant branch channel portion is provided, and the number of refrigerant branch channel portions in each refrigerant distributor unit is equal. The heat exchanger according to any one of claims 1 to 10.   12. The length of each flow path, the cross-sectional shape of each flow path, and the total sum of the bending angles of each flow path in the plurality of refrigerant branch flow path portions provided are equalized. The heat exchanger as described in any of the above.   The heat flowing into the heat exchanger main body is at least one of the length of each flow path in the plurality of refrigerant branch flow path sections provided, the cross-sectional shape of each flow path, and the total bending angle of each flow path. The heat exchanger according to any one of claims 1 to 11, wherein the heat exchanger is changed according to a velocity distribution of air to be exchanged.   Provided in the plate-like distribution member that constitutes the refrigerant distributor is a refrigerant gas merging portion for collecting refrigerant gas that is distributed by the refrigerant branch flow path portion and supplied to the heat exchanger main body and flows out of the heat exchanger main body. The heat exchanger according to any one of claims 1 to 13, wherein the heat exchanger is provided.   The refrigerant distributor is constituted by a plurality of plate-like members including plate-like distribution members that are superposed on each other, and a refrigerant gas merging portion for collecting the refrigerant gas is separated from the plate-like distribution member. The heat exchanger according to claim 1, wherein the heat exchanger is provided in the heat exchanger.   A refrigerant having a refrigerant throttling function for supplying a refrigerant at a predetermined flow rate to a plurality of predetermined flow path portions in the heat exchanger main body, a refrigerant distribution part for dividing the refrigerant from the refrigerant inlet, and the refrigerant divided by the refrigerant distribution part A plate-like distribution member having a branch flow channel portion; and a plurality of plate-shaped distribution members that are arranged to overlap with the plate-shaped distribution member and communicate with a predetermined flow channel portion of the plate-shaped distribution member to a predetermined flow channel portion of the heat exchanger body. A plate-like connecting member having an opening connection portion, a plate-like communicating member superposed on the other surface of the plate-like distribution member disposed on one side of the heat exchanger main body, and one surface of the heat exchanger main body side The plate-like connecting member disposed on the other side of the plate-like connecting member is superposed on the plate-like connecting member, the plate-like distributing member, and the refrigerant communication port provided in the plate-like connecting member. A plate-like joining member provided with a joining portion communicating with refrigerant outlets from a plurality of places on the exchanger body, and one surface is polymerized on the other surface of the plate-like joining member disposed on the heat exchanger body side. Refrigerant introduction comprising a plate-like adherent member, wherein the plate-like adherent member communicates with a refrigerant inlet of the plate-like distribution member via a refrigerant communication port provided in the plate-like joining member and the plate-like communicating member. The heat exchanger according to claim 15, wherein a refrigerant outlet that communicates with a junction of the plate-like junction member is provided along with an opening.   The heat exchanger according to any one of claims 1 to 13, further comprising a refrigerant gas merging portion separately from the plate-like member constituting the refrigerant distributor.   The heat according to any one of claims 1 to 17, wherein a non-circular tube having pores therein is used as a heat transfer tube of a heat exchanger body to which refrigerant is supplied from the refrigerant distributor. Exchanger. The heat exchanger according to any one of claims 1 to 17, wherein a thin tube having an inner diameter of 3 mm or less is used as a heat transfer tube of a heat exchanger body to which a refrigerant is supplied from the refrigerant distributor.

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