JP6634934B2 - Heat exchangers and air conditioners - Google Patents

Description

  The present invention relates to a heat exchanger having fins and an air conditioner using the heat exchanger.

  A fin laminated body in which a plurality of fins are laminated at intervals, a tube (flow path) penetrating the fin laminated body in the fin laminating direction, and a fluid is supplied to a flow path in the tube at an end of the fin laminated body. There is a fin tube type heat exchanger composed of a supply section and a supply section. In such a heat exchanger, a structure in which two flow paths are connected by a U-shaped tube at an end of the fin laminate is known. Further, instead of a U-shaped tube, a structure in which two flow paths are connected by a concave portion formed in an end plate as in Patent Document 1 or Patent Document 2 is also known.

JP-A-59-229194 JP 2014-513788 A

  As in Patent Documents 1 and 2, a structure in which a concave portion is provided in an end plate and a flow path is connected in the concave portion has a shorter projecting length and is more compact than a connection using a U-shaped tube. There are advantages such as improved productivity. However, compared to the connection using a U-shaped tube or the like, the fluid flowing into the concave portion from the flow path is bent at a steep angle, so that there is a problem that a vortex or the like is generated and a pressure loss is likely to occur.

  Therefore, an object of the present application is to realize a heat exchanger that can reduce pressure loss even when a connecting member having such a concave portion is used. Moreover, it aims at realizing an air conditioner with small loss using such a heat exchanger.

The heat exchanger of the present invention includes a fin laminate in which a plurality of fins are laminated in a first direction at intervals;
A first flow path through which the fluid flows through the plurality of fins;
A connection member having a recess, wherein a periphery of an opening of the recess is fixed to an end of the fin laminate in the first direction.
A heat exchanger in which the recess covers the first opening of the first flow passage, and the fluid flowing into the recess from the first opening flows in the recess in a second direction intersecting with the first direction; And
A first flow guide having a first inclined surface is provided beside the first opening on the side of the second direction, the distance in the second direction increasing with distance from the first opening in the first direction. ,
The first inclined surface has a groove extending from the first opening in the second direction,
Alternatively, a third inclined surface that is inclined with respect to the first direction and is opposed to the first inclined surface of the first flow guide is provided on a side of the first opening opposite to the first flow guide. Comprising a second flow guide;
Alternatively, the first flow path is constituted by a tube or a connected collar portion, and the first flow guide is constituted by at least a part of the collar portion or the tube protruding into the recess .

  An air conditioner of the present invention includes the above heat exchanger, a utilization circuit for supplying a fluid to the heat exchanger, and a heat source for heating or cooling the fluid.

  Since the heat exchanger of the present invention includes the flow guide having the first inclined surface in the connection member, the fluid flowing into the concave portion has a gentle bend, and can reduce the pressure loss.

  Since the air conditioner of the present invention includes the above-described heat exchanger, the pressure loss can be reduced, so that the loss of the utilization circuit is reduced.

FIG. 2 is a perspective view illustrating the entire heat exchanger according to the first embodiment. FIG. 2 is a perspective view illustrating the entire heat exchanger according to the first embodiment. FIG. 3 is a cross-sectional view illustrating an internal structure of the heat exchanger according to the first embodiment. FIG. 3 is a cross-sectional view illustrating an internal structure of the heat exchanger according to the first embodiment. FIG. 3 is a partial cross-sectional view for explaining a configuration of the heat exchanger according to the first embodiment. FIG. 4 is a schematic diagram illustrating the operation of the inclined surface 7 according to the first embodiment. FIG. 4 is a schematic diagram illustrating the operation of the inclined surface 7 according to the first embodiment. FIG. 3 is a perspective view illustrating an example of an arrangement of each element in a connection member 6 according to the first embodiment. FIG. 2 is a configuration diagram of an air conditioner 100 using the heat exchanger 10 of the first embodiment. FIG. 4 is a cross-sectional view illustrating a modification of the heat exchanger according to the first embodiment. FIG. 4 is a cross-sectional view illustrating a modification of the heat exchanger according to the first embodiment. FIG. 4 is a cross-sectional view illustrating a modification of the heat exchanger according to the first embodiment. FIG. 4 is a cross-sectional view illustrating a modification of the heat exchanger according to the first embodiment. FIG. 9 is a partial cross-sectional view for illustrating a configuration of a heat exchanger 10 according to a second embodiment. FIG. 10 is a partial cross-sectional view for describing a configuration of a heat exchanger 10 according to a modification of the second embodiment. FIG. 10 is a partial cross-sectional view for describing a configuration of a heat exchanger 10 according to a third embodiment. FIG. 13 is a perspective view illustrating an example of an inclined surface 7 of a heat exchanger 10 according to a third embodiment. FIG. 14 is a partial cross-sectional view illustrating a configuration of a modification of the heat exchanger 10 according to the third embodiment. FIG. 21 is a perspective view illustrating an example of a modification of the third embodiment. FIG. 14 is a partial cross-sectional view for describing a configuration of a heat exchanger according to a fourth embodiment. FIG. 13 is a perspective view illustrating a heat exchanger according to a fourth embodiment. FIG. 15 is a partial cross-sectional view for describing a configuration of a modification of the heat exchanger according to Embodiment 4.

  Hereinafter, a heat exchanger and an air conditioner of the present invention will be described with reference to the drawings. In different embodiments, components having the same functions are denoted by the same reference numerals, and description thereof will be omitted. In addition, of the following embodiments, a structure in which a structure, a material, or the like described in one embodiment is replaced with, for example, a structure, a material, or the like described in another embodiment as long as technical inconsistency does not occur. Are also included in the present invention.

<First Embodiment>
FIG. 1 is a perspective view showing a heat exchanger according to Embodiment 1 of the present invention. FIG. 2 is a perspective view of the heat exchanger viewed from a direction different from FIG. FIG. 3 is a sectional view illustrating the internal structure of the heat exchanger. FIG. 4 is a cross-sectional view seen from a direction different from FIG. 3, and is a cross-sectional view obtained by cutting along a plane including a dotted line AA in FIG. The heat exchanger according to the first embodiment has a plurality of fins that overlap with an interval and a flow path penetrating the fins, and a fluid (liquid or gas) flowing in the flow path, air around the fins, and heat Exchange. In the following, description will be made assuming that the fluid is mainly a liquid such as water, but the fluid may be a gas such as water vapor or a mixture of a gas and a liquid. Wind is sent to the fins by a blower or the like, or air by natural convection flows, thereby promoting heat exchange with the air. The white arrows in the figure indicate the flow of air (WF) or the flow of refrigerant entering and exiting the heat exchanger (RF). Further, broken arrows in the drawing indicate the direction in which the fluid flows in the flow path.

  The heat exchanger 10 has a fin laminate 1 in which a plurality of fins 1a are laminated at intervals in one direction. The fin 1a is formed of a generally flat thin plate, and its main surface may have small irregularities, cut-and-raised portions, or the like on its surface. The main surfaces of the adjacent fins 1a are substantially parallel. At the both ends in the stacking direction of the fin stack 1, plate members 1b are stacked in parallel with the fins 1a. The plate 1b may be a plate thicker than the fin 1a, or may be the same member as the fin 1a.

  As shown in FIGS. 3 and 4, the heat exchanger 10 includes a flow path 3 (first flow path 3A and second flow path 3B) that penetrates the plurality of fins 1a in the stacking direction inside the fin laminate 1. Have. The first flow path 3A and the second flow path 3B are each linear, and both are substantially parallel.

  A connection member is provided at a position corresponding to the opening at the end of the first flow path 3A and the end of the second flow path 3B at the end of the fin laminate 1. The connecting member communicates with the plurality of flow paths 3 at one end of the fin laminate 1 to flow fluid into or out of the plurality of flow paths 3. The connection member includes, for example, a connection member 6 that connects the first flow path 3A and the second flow path 3B, a connection member 4 that distributes fluid sent from a pipe connected from the outside to the plurality of flow paths 3, A connection member 5 for connecting the fluids flowing out of the plurality of flow paths 3 so as to collectively send the fluid to an external pipe; The connection member 6 is a member that connects the first flow path 3A and the second flow path 3B so as to be folded at the ends.

  The connection members 4, 5, 6 have recesses 4a, 5a, 6a and flanges 4b, 5b, 6b formed around the openings of the recesses. The recesses 4 a, 5 a, 6 a cover the opening of the flow channel 3 at one end of the fin laminate 1. The flange portions 4b, 5b, 6b are fixed to the outermost plate 1b of the fin laminate 1. A space formed between the outermost plate member and the concave portion serves as a connection flow path that connects the plurality of flow paths 3.

  A fluid is sent to the heat exchanger 10 by applying pressure from a pump or the like so that fluid is sent from an external pipe 14 and fluid is sucked out of the other pipe 15. The fluid flowing from the external pipe 14 flows in the recess 4a of the connection member 4 in a direction parallel to the main surface of the plate 1b or the fin 1a, and then flows from the opening 9C into the first flow path 3A serving as an outward path. The heat of the fluid flowing through the first flow path 3A is transmitted from the first flow path 3A to the plurality of fins 1a, and the heat is transmitted to the air on the surface of the fin 1a. At the end of the fin laminate 1 opposite to the connection member 4, there is a connection member 6 at which the fluid flows out of the first opening 9A of the first flow path 3A. After changing the direction of the fluid flowing in the connection member 6 in a direction parallel to the main surface of the plate 1b or the fin 1a, the fluid flows from the second opening 9B into the second flow path 3B serving as a return path. The fluid flowing through the second flow path 3B flows out of the opening 9D into the connection member 5 after performing heat exchange with the air through the fins 1a as in the first flow path 3A. The fluid applied to the connecting member 5 is changed in direction parallel to the main surface of the fin 1a, flows along the main surface of the fin 1a, and is then sent out from the external pipe 15. Thus, the fluid flows back and forth in the flow path 3 inside the fin laminate 1 and exchanges heat with the air flowing through the fin 1a.

  In the above description, the inflow fluid is configured to pass through the first flow path 3A and the second flow path 3B, that is, reciprocate once between both ends of the fin laminate 1, and flow out. The number of reciprocations can be variously changed. For example, the connection member 4 may be provided at one end and the connection member 5 may be provided at the other end, so that the first flow path 3A flows in one direction and then flows out. Also, connecting members 6 are installed at both ends, and reciprocated between both ends a plurality of times so that the first flow path 3A flows to the second flow path 3B and the second flow path 3B flows to another third flow path 3C. The configuration may be such that Further, if at least a connecting member having a concave portion is used, all of the connecting members 4, 5, and 6 do not need to be members having a concave portion. For example, the connecting member 6 may be used only at the portion connecting the two flow paths, and a tubular header may be used instead of the connecting members 4 and 5.

  FIG. 5 is a partial cross-sectional view for explaining the configuration of the heat exchanger of the first embodiment, and is an enlarged view of the left part of FIG. This figure shows the internal structure of the connection member 6 that connects the first flow path 3A and the second flow path 3B so as to be folded.

  In the heat exchanger 10 of the first embodiment, the first flow path 3A and the second flow path 3B are formed by the collar portion 11 formed on the fin 1a. The fin 1a is a thin plate made of a metal material having good heat conductivity, such as aluminum, copper, or an alloy thereof. The collar portion 11 is a portion formed on the thin fin 1a by press working or the like, and is opened at one side of the fin 1a so as to protrude in a cylindrical shape. The collar portion 11 has a tapered shape in which the outer diameter at the distal end side protrudes thinly from the main surface of the fin 1a serving as the root, and the distal end is opened. In the flow path 3 (the first flow path 3A and the second flow path 3B), the fins 1a are overlapped with each other, and the tip of the collar portion 11 of one fin 1a is inserted into the opening of the collar portion 11 of the other fin 1a. It is made by connecting the collar parts 11. The inside of the connected collar portion 11 is the flow path 3.

  By the connection of the collar portions 11, the interval between the fins 1a in the stacking direction is kept substantially constant. The interval between the fins 1a is determined by the depth at which the collar portion 11 is inserted, and the depth is determined by the processing shape, size, and the like of the collar portion 11. For example, the thickness of the fin 1a can be 0.2 to 1 mm, and the interval between the fins 1a can be 1 to 5 mm.

  Further, a collar portion 12 is also formed on the endmost plate 1b in the laminating direction of the fin laminate 1 in the same manner as the fin 1a, and the collar portion 12 is connected to the collar portion 11 of the fin 1a to form the flow path 3 (the Part of the first flow path 3A and the second flow path 3B) is formed.

  The inner surface connecting the collar portions 11 and 12 is covered with a resin layer 23. The resin layer 23 seals the gap between the connected collar portions 11 and 12 and protects the inside of the collar portions 11 and 12. In addition, the resin layer 23 mechanically reinforces the connection between the collar portions 11 and 12.

  When the main component of the fluid flowing through the flow path 3 is water and the main component of the fin 1a is a material that is easily corroded by water, such as aluminum, the resin layer 23 is formed on the inner surfaces of the collar portions 11 and 12. Prevent corrosion. Heat is transmitted from the fluid to the fins 1 a via the resin layer 23. Since the thermal conductivity of the resin layer 23 is smaller than that of a metal, the thickness of the resin layer 23 is preferably as thin as possible while ensuring durability. For example, the thickness of the resin layer 23 in the main part may be set to 50 μm or less, 10 μm or more.

  Note that the tip portion of the collar portion 11 is a portion where a steep step occurs between the collar portions 11, and it is desirable that the thickness of the resin layer 23 be greater than 50 μm at that portion. There may be some flow turbulence inside the flow path 3 to promote heat exchange. However, since the turbulence causes a pressure loss, the connection step between the collar portions 11 is changed so that appropriate turbulence occurs. 23 may be made smooth. As described above, the resin layer 23 can reduce the pressure loss by making the step moderately gentle.

  The connecting member 6 is fixed to the endmost plate 1b of the fin laminate 1 by a flange 6b. The opening of the recess 6a of the connection member 6 faces the plate 1b. A space closed by the flange 6b is formed between the recess 6a and the plate 1b. The first opening 9A of the first flow path 3A and the second opening 9B of the second flow path 3B are connected to this space and are connected as a flow path. As described above, since the plurality of flow paths having ends at the same plate 1b are connected by using the recess 6a, the length protruding from the end of the fin laminate 1 is short, and compact connection is possible.

  The connection member 6 can be made of a metal containing aluminum as a main component similarly to the fin 1a. It is preferable that the inner surface of the concave portion 6a of the connection member 6 be covered with the resin layer 26 as in the case of the collar portions 11 and 12. The plate 1b can be made of a metal containing aluminum as a main component, similarly to the fin 1a. It is preferable that the surface of the plate member 1b facing the concave portion 6a is covered with the resin layer 22. The plate 1b and the flange 6b may be fixed by the resin layer 26, the resin layer 22, or the like.

  When the connecting members 4, 5, and 6 having such concave portions are used, the flow direction of the fluid greatly changes inside the connecting members 4, 5, and 6, and a vortex is likely to be generated. A first flow guide 7 having an inclined surface is provided beside the opening 9 (the first opening 9A and the like) of the flow path 3A and the like.

  The flow path 3 linearly extends in the fin laminate 1 to the opening 9. Assuming that the straight line direction of the flow path 3 is the flow path direction, the first flow guide 7 has an inclined surface inclined at less than 90 degrees with respect to the flow path direction. The inclined surface of the first flow guide 7 is inclined away from a position where the flow path extends in the flow direction as the distance from the opening 9 increases in the flow direction. In addition, the inclined surface is inclined such that the distance in the flow direction in the connecting member 6 that is orthogonal to the flow direction increases as the distance from the opening 9 in the flow direction increases. The inclined surface includes a first inclined surface 7A provided beside the first opening 9A of the first flow path 3A, a second inclined surface 7B provided beside the second opening 9B of the second flow path 3B, and the like. is there. The first flow guide 7 may be constituted by not only one member but also a plurality of members. Although the first flow guide 7 is provided in the two openings in the figure, either one may be provided. The first flow guide 7 is provided between one opening and the other when the inside of the concave portion 6a is viewed in the flow path direction. In the case of the connecting member 6, the first flow guide 7 is installed in a shape symmetrical with respect to the two flow paths 3A, 3B because it is to be turned back by the two flow paths 3A, 3B. In the connection members 4 and 5, as shown in FIG. 4, a first flow guide 7 which is inclined in the same direction as the flow in the direction in which the connection member 4 extends is provided in each opening of the plurality of flow paths 3. And good. The first flow guide 7 can be provided as a surface shape of various members, and the drawing shows a case where a plate material is used.

  6 and 7 are schematic diagrams illustrating the operation of the first flow guide 7 according to the first embodiment. FIG. 6 shows the flow of the fluid without the first flow guide 7, and FIG. 7 shows the flow of the fluid without the first flow guide 7. In both cases, the flow is common in that it is bent in a U-shape in the recess 6a. This flow is caused by a pressure difference applied to two flow paths connected to the connection member 6. As shown in FIG. 6, when the fluid enters the recess 6a from the first flow path 3A without the first flow guide 7, there is an approximately right angle in the flow direction with the plate 1b. The part is swirled by this angle. On the other hand, as shown in FIG. 7, when the fluid enters the recess 6a from the first flow path 3A in a state where the first flow guide 7 is present, the bent portion has an obtuse angle, and the direction of the flow path changes slowly. And the generation of vortices is suppressed. In addition, since the flow of the fluid tends to flow along the wall, a part of the fluid flows along the first flow guide 7 in the case of FIG. In the first embodiment, the first opening 9A has the first inclined surface 7A provided only on the second opening 9B side, so that the flow out of the first opening 9A easily flows in the direction of the second opening 9B. Becomes Thus, the first flow guide 7 functions as a guide for smoothing the flow of the fluid. The first flow guide 7 is a surface of a plate or member provided in the recess 6a. By suppressing the generation of the vortex, an increase in pressure loss can be suppressed.

  The first flow guide 7 preferably has a surface having an angle of, for example, 30 to 60 degrees with respect to the flow path direction. Thereby, the side of the opening of the first flow path 3A can have an obtuse angle of 120 to 150 degrees. Most preferably, the first flow guide 7 is a surface that continuously connects to the edge of the opening at the end of the first flow path 3A, but a similar effect can be obtained even if it is slightly away from the edge of the opening. For example, the distance away from the edge of the opening may be within 1/4 of the diameter of the first flow path 3A. Further, the length of the first flow guide 7 can be appropriately changed as long as the flow passage area in the concave portion 6a can be ensured to be at least larger than the flow passage areas of the first flow passage 3A and the second flow passage 3B. When the length of the first flow guide 7 is equal to or larger than the diameter of the flow path 3, the flow along the first flow guide 7 can be excellent.

  Although FIG. 7 shows an example in which the second flow path 3A is provided only near the outlet, the second inclined surface 7B may be provided near the entrance of the second flow path 3B as shown in FIG. Good. Since the portion flowing into the second flow path 3B from the inside of the concave portion 6a also has a right angle, this can be changed to an obtuse bend so that the fluid entering the second flow path 3B can flow smoothly. The configuration in which both the first flow guides 7 are provided is particularly effective in a system in which the heat exchanger 10 flows in both directions such that the flow direction between the first flow path 3A and the second flow path 3B changes.

  FIG. 8 is a perspective view illustrating an example of an arrangement of each element in the connection member 6 according to the first embodiment. In the drawing, the flow path direction is X (first direction), the direction connecting the first opening 9A and the second opening 9B is Y (second direction), and the direction orthogonal thereto is Z (third direction). ). The first flow guide 7 in the figure is formed by a plate elongated in the Z direction. Although the plate is substantially rectangular, other shapes may be used. This plate is fixed at both ends in the longitudinal direction in the concave portion 6a and is held so as to keep an appropriate angle with the flow direction X. The first flow guide 7 may be fixed to the plate 1b. The height of the first flow guide 7 in the X direction is lower than the height in the X direction in the concave portion 6a, and is, for example, about half the height in the concave portion 6a. The first flow guide 7 exists in the recess 6a toward the plate 1b, and a flow path from the first opening 9A to the second opening 9B is secured in the recess 6a on the side opposite to the plate 1b. . Since the recess 6a has a size several times or more in the X direction and the Z direction compared to the diameter of the first opening 9A or the second opening 9B, the cross-sectional area of the flow path in the Y direction is much larger than that of the flow path 3. large. The width of the inclined surface 7A of the first flow guide 7 in the Z direction is also larger than the width of the first opening 9A. Therefore, even if the X direction in the concave portion 6a is narrowed by the installation of the first flow guide 7, a sufficiently large flow path cross-sectional area can be secured as compared with the first opening 9A, and the flow path cross-sectional area is narrow. There is no effect of increasing losses.

  FIG. 9 is a configuration diagram of an air conditioner 100 using the heat exchanger 10 of the first embodiment. A heat source circuit 30 and a utilization circuit 40 are provided, and heat generated in the heat source circuit 30 is exchanged with the utilization circuit 40 by the intermediate heat exchanger 50 and used for adjusting the indoor temperature. The utilization circuit 40 is a circuit in which the fluid circulates and flows. The heat exchanger 10 of the first embodiment can be suitably used in the utilization circuit 40 as the indoor heat exchanger 43 for exchanging heat between the temperature of the fluid and the temperature of the indoor air.

  Here, an example of a heat pump using a refrigerant cycle is shown as the heat source circuit 30. A pipe 39 is connected to the compressor 31, the condenser, the expansion valve 33, and the evaporator so that the refrigerant flows in this order. A switch 34 for switching the flow to the refrigerant is provided so that one of the condenser and the evaporator is the outdoor heat exchanger 32 and the other is the intermediate heat exchanger 50. In the figure, the intermediate heat exchanger 50 functions as a condenser in the direction in which the refrigerant flows as indicated by the solid line arrow, and the heating operation is performed. In the utilization circuit 40, the intermediate heat exchanger 50 functions as an evaporator in the direction in which the refrigerant flows in the direction indicated by the broken line arrow in the drawing, and the cooling operation is performed. The outdoor heat exchanger 32 exchanges heat between the refrigerant and the outdoor air, and heat exchange with the air is promoted by the wind from the blower 35. Instead of a heat pump using a refrigerant cycle, a heat source that heats or cools a fluid, such as a combustion system or a device that uses local heat supply, may be used.

  The use circuit 40 includes a pipe 49 that circulates between the intermediate heat exchanger 50 and the indoor heat exchanger 43 and through which the use-side refrigerant flows, and a pump 41 provided in the pipe 49. The use side refrigerant (fluid) is supplied to the indoor heat exchanger 43 (heat exchanger 10) by the pump 41. The use-side refrigerant is water, an antifreeze containing water, or the like. The intermediate heat exchanger 50 exchanges heat between the refrigerant on the heat source side and the use-side refrigerant, and may be a plate heat exchanger, a double tube heat exchanger, or the like. The indoor heat exchanger 43 exchanges heat between the use-side refrigerant containing water and the air, and the air is blown by the blower 45 to promote the heat exchange with the indoor air. In addition, there is a control device 60 that adjusts the operation according to a request from the room. The control device 60 adjusts the operation of the switch 34, the compressor 31, the blower 35, and the expansion valve 33 of the heat source circuit 30, and the operation of the pump 41 and the blower 43 of the utilization circuit 40 as required.

  The pressure applied to the fluid in the indoor heat exchanger 43 is a relatively low pressure from the pump 41, for example, about 0.1 to 0.5 MPa. In a flow path having such a low pressure, the influence of pressure loss in the flow path is likely to increase. When the pressure loss inside the heat exchanger increases, the use-side refrigerant to be supplied must be set to a high pressure, and a high-performance pump 41 and a highly reliable resin layer and a bonding portion that can withstand the high pressure are required. In the heat exchanger 10 according to the first embodiment, since the pressure loss is reduced by the first flow guide 7, such a problem hardly occurs. Therefore, the heat exchanger 10 of the first embodiment is suitable for the indoor heat exchanger 43 of such a system.

  Next, a modification of the heat exchanger of the first embodiment will be described. 10 to 11 are cross-sectional views showing modified examples of the heat exchanger according to Embodiment 1, and correspond to the same cross-sectional views as FIG.

  The heat exchanger shown in FIG. 10 is configured such that the inclined surfaces 7A and 7B of the heat exchanger shown in FIG. 5 are curved surfaces. In the heat exchanger of FIG. 10, the first flow guide 7 is a curved surface in which the distance away from the extension obtained by extending the flow path 3 as a straight line increases with increasing distance from the opening 9 in the flow path direction. Therefore, the fluid entering through the opening 9 has a smooth change along the curved surface of the first flow guide 7 so that the direction gradually becomes parallel to the plate 1b, and the effect of reducing the loss is increased.

  FIG. 11 is a cross-sectional view showing a modified example in which the first flow guide 7 of the heat exchanger shown in FIG. The shape of the curved surface is similar to that of the heat exchanger shown in FIG. 10, but the heat exchanger shown in FIG. 11 has two inclined surfaces 7A and 7B formed as continuous surfaces by one plate. The whole is formed of a U-shaped curved surface that continuously and smoothly connects the sides of two continuous openings, and the surface facing the first opening 9A side among the curved surfaces is the first inclined surface 7A, the second inclined surface. The surface facing the opening 9B is the second inclined surface 7B. Since it is composed of one member, installation is simplified, and since the two openings are continuously connected, the flow is not disturbed at a portion where the first inclined surface 7A and the second inclined surface 7B are interrupted. The effect of further reducing the loss increases.

  FIG. 12 is a cross-sectional view showing still another modification in which the first flow guide 7 of the heat exchanger shown in FIG. It is the same as FIG. 11 in that there is a U-shaped curved surface that continuously and smoothly connects the sides of the two openings, but this curved surface (the first inclined surface 7A and the second inclined surface 7B) is a block-shaped member 15. Part of the surface. The opposite side to the curved surface is the same flat surface as the plate member 1b, and is adhered and fixed to the plate member 1b, that is, the end of the fin laminate 1. The block-shaped member 15 can be made of, for example, resin. When the first flow guide 7 was formed of a plate, there was a space between the plate and the plate 1b where a fluid could enter. However, in the structure of FIG. 12, the fluid entered between the plate 1b and the first flow guide 7. Since this does not occur, the flow is less likely to be disturbed, and the effect of reducing the loss is increased.

  FIG. 13 is a sectional view showing still another modification in which the first flow guide 7 of the heat exchanger shown in FIG. 5 is formed of a plate material. The plate is deformed so as to have a convex shape between the two openings toward the concave portion 6a. The convex shape has a U-shaped curved surface that continuously and smoothly connects between the sides of the two openings. Thereby, the surface of the convex portion has an inclined surface, and is excellent in the effect of reducing the loss as in the case where the block-shaped member 15 of FIG. 12 is installed. Further, the number of members to be fixed in the concave portion 6a is reduced, and cost reduction can be realized.

<Embodiment 2>
FIG. 14 is a partial cross-sectional view illustrating the configuration of heat exchanger 10 according to the second embodiment, and is a cross-sectional view corresponding to FIG. 5 in the first embodiment. The heat exchanger 10 of the second embodiment has, in addition to the inclined surfaces 7A, 7B, a second inclined surface 8A, 8B near the edge of the opening 9 (9A, 9B) opposite to the inclined surface 7. A flow guide 8 is provided. In each opening, the direction in which the inclined surfaces 8A, 8B of the second flow guide 8 are inclined with respect to the flow path direction is the same as the direction in which the inclined surfaces 7A, 7B of the first flow guide 7 are inclined with respect to the flow path direction. Is the same. The third inclined surface 8A of the second flow guide 8 is opposed to the first inclined surface 7A of the first flow guide 7, and the fourth inclined surface 8B of the second flow guide 8 is the third inclined surface of the first flow guide 7. It faces the surface 7B. The opening 9 side of the second flow guide 8 is close to the edge of the opening 9, and the inclined surface of the second flow guide 8 exists in the extending direction of the flow path.

  Of the fluid that has entered the recess 6a from the first flow path 3A via the first opening 9A, the fluid flowing on the side closer to the second opening 9B is the second opening along the inclined surface 7A as described above. Turn to 9B side. When the flow velocity entering the concave portion 6a is low, the fluid entering the concave portion 6a from the side far from the second opening 9B also moves toward the second opening 9B in accordance with the flow of the fluid near the second opening 9B. Bend. However, when the flow velocity is high, the fluid that has entered the recess 6a proceeds in the direction of the first flow path 3A without bending. The fluid having such a flow may collide with the inner surface of the concave portion 6a and disturb the flow. Therefore, in the second embodiment, by providing the third inclined surface 8A that is bent toward the second opening 9B on the extension of the first passage 3A in the flow direction, the second opening is not disturbed. Since it can proceed to the 9B side, the effect of reducing loss is excellent.

  Further, in the second embodiment, since the fourth inclined surface 8B is provided on the second opening 9B on the side opposite to the first opening 9A, the fluid flowing in the recess 6a can be guided to the second flow path 3B. Since it is possible, the effect of reducing the loss is excellent.

  The third inclined surface 8A and the fourth inclined surface 8B can be formed by fixing a plate member or a block-shaped member to the concave portion 6a or the plate member 1b.

  FIG. 15 is a partial cross-sectional view illustrating the configuration of heat exchanger 10 according to a modification of the second embodiment. The third inclined surface 8A and the fourth inclined surface 8B of this modified example are formed of smoothly connected continuous surfaces, similarly to the case of the first inclined surface 7A and the second inclined surface 7B of FIG. As a result, the fluid flows between the two inclined surfaces of the first flow guide 7 that connects near the first opening 9A and the second opening 9B, and the second flow guide 8 that connects far. Since the second flow guide 8 is formed as a continuous surface, the fluid does not intrude further outside the second flow guide 8 to cause a flow loss, and the effect of reducing the loss is great.

<Embodiment 3>
FIG. 16 is a partial cross-sectional view illustrating the configuration of heat exchanger 10 according to the third embodiment, and is a cross-sectional view corresponding to FIG. 5 in the first embodiment. In the above embodiment, an example of the structure in which the flow path 3 does not protrude into the connection member 6 has been described. The third embodiment has a structure in which the flow path 3 (3A, 3B) protrudes from the plate 1b in the connection member 6. Although the figure shows the case where the collar portion 11 constituting the flow path 3 protrudes, the flow path may be formed of a pipe and the end of the pipe may protrude. In such a structure, the opening at the end of the flow path 3 (3A, 3B) corresponds to the first opening 9A and the second opening 9B. With such a structure, the problem such as generation of a vortex as shown in FIG. 6 is unlikely to occur, but there is a problem that the fluid travels straight in the direction in which the flow path extends and collides with the recess 6a. Therefore, by providing the inclined surfaces 7A and 7B described in the above embodiment near the first opening 9A at the end of the flow path 3 (3A and 3B), the flow coming out from the end can be made the first flow guide. As a flow along 7, it may be bent toward the second opening 9 </ b> B. Such an inclined surface can be formed on the surface of the plate material or the surface of the block-shaped member 15 and installed in the recess 6a.

  FIG. 17 is a perspective view showing a state where a block-shaped member 15 is installed in the recess 6a as an example of the first flow guide 7 of the heat exchanger 10 of the third embodiment. On the surface of the block-shaped member 15, a groove 16 is provided extending from the first opening 9A toward the second opening 9B (Y direction). Further, the position of the first opening 9A is on the extension of the groove 16, and the height of the first opening 9A in the X direction near the side of the first opening 9A (height at which the first flow path 3A protrudes). And the height of the groove 16 in the X direction is substantially the same. Although the figure shows the first flow path 3A side, the second flow path 3B is also an extension of the groove 16 and has the same height as the groove. Thereby, the fluid that has flowed out of the first opening 9A flows smoothly along the groove 16 to the second opening 9B. Since the flow is prevented from diffusing in the Z direction by providing the groove 16, it is possible to prevent a loss caused by the flow diffusing.

  FIG. 18 is a partial cross-sectional view illustrating a configuration of a modification of the heat exchanger 10 according to the third embodiment. The flow path 3 (3A, 3B) of this modified example is formed of a tube, and has a structure in which the end of the tube protrudes. In this modification, the first flow guide 7 is formed by bending a plate material.

  FIG. 19 is a perspective view for explaining an example of the arrangement of each element in the connection member 6 according to a modification of the third embodiment. The plate material has a width in the Z direction larger than the first opening 9A and the second opening 9B, and a length in the Y direction longer than the length from the first opening 9A to the second opening 9B. It is formed by bending so as to be convex. The bent portion in the X direction forms a slope, and a hole or a cut is formed in the bent portion so that the distal ends of the first opening 9A and the second opening 9B enter. On the side of the first opening 9A on the side of the second opening 9B, and on the side of the second opening 9B on the side of the first opening 9A, the first inclined surface 7A and the second inclined surface 7B formed by the plate material are substantially the same. It is made to be high. Therefore, the flow loss can be reduced by the first inclined surface 7A and the second inclined surface 7B as in the configuration described above.

  Further, in the case of a structure in which the flow path 3 protrudes as in the third embodiment, a member configuring the first flow guide 7 may be fixed to a protruding portion of the flow path 3. As shown in FIG. 17 and FIG. 19, the structure in which the flow path 3 is sandwiched in the Z direction by the inclined portion prevents displacement of the first flow guide 7 with respect to the opening and fixes the first flow guide 7. It can be robust.

  Although the groove 16 shown in FIG. 17 is not formed in the plate shown in FIG. 19, the groove 16 may be provided in the plate shown in FIG. 19 or the inclined surface in the above embodiment.

<Embodiment 4>
FIG. 20 is a partial cross-sectional view for illustrating the configuration of the heat exchanger according to the fourth embodiment, and is a cross-sectional view corresponding to FIG. 5 in the first embodiment. The fourth embodiment has a structure in which the collar portion 11 constituting the flow path 3 protrudes into the connection member 6, and a partially deformed portion of the collar portion 11 forms a guide having an inclined surface. .

  FIG. 21 is a perspective view showing a state where a part of the collar portion 11 of the heat exchanger according to the fourth embodiment constitutes the first flow guide 7. As shown in the figure, a part of the protruding collar portion 11 has a plurality of cuts from the end, and has a slope 7A that is bent between the cuts toward the other opening (Y direction). are doing. Since a part of the collar portion 11 is bent and widened by the cut, the base of the cut corresponds to the first opening 9A.

  In addition, a surface located opposite to the inclined surface 7A is bent in the same direction as the inclined surface 7A, thereby forming the same structure as the inclined surface 8A described in the second embodiment.

  In the fourth embodiment, the first flow guide 7 or the second flow guide 8 is configured by using at least a part of the flow path protruding into the connection member 6, so that the material is reduced in addition to the effect of reducing the loss. Therefore, the effect that the cost can be reduced is obtained.

  FIG. 22 is a partial cross-sectional view illustrating a configuration of a modified example of heat exchanger 10 of the fourth embodiment. The flow path 3 of this modification is a tube, and a portion of the tube protruding into the connecting member 6 is bent, and the bent portion becomes the first flow guide 7 or the second flow guide 8 having an inclined surface. ing. The boundary between the straight portion penetrating the fin 1a and the bent portion of the tube tip corresponds to the openings 9A and 9B of each flow path. Of the inner wall of the bent portion of one tube, the surface on the other opening side corresponds to the first inclined surface 7A and the second inclined surface 7B, and the surface on the side farther from the other opening is the third inclined surface. The surface 8A corresponds to the fourth inclined surface 8B. The bent tip of the tube is open in the recess 6 a of the connecting member 6. With such a shape, the fluid from the first flow path 3A in the tube is bent toward the third flow path 3B by the first inclined surface 7A and the third inclined surface 8A and enters the concave portion 6a. Further, the fluid that has entered the third flow path 3B from inside the recess 6a is bent by the second inclined surface 7B and the third inclined surface 8B, and flows into the straight portion of the third flow path 3B. In particular, since the first inclined surface 7A, the third inclined surface 8A, the second inclined surface 7B, and the third inclined surface 8B are formed by smooth curved surfaces as shown in the drawing, the flow is close to that when the connection is made by a U-shaped tube. Therefore, a turbulence hardly occurs and a low-loss heat exchanger can be obtained. In addition, since the flow guide is formed by using a part of the tube forming the flow path in the same manner as the collar portion 11, another material is not required, and an increase in cost can be prevented.

  INDUSTRIAL APPLICABILITY The heat exchanger and the air conditioner of the present invention are useful in that loss when a fluid such as water is used can be reduced.

Reference Signs List 1 fin laminate, 1a fin, 1b plate, 3 flow path, 3A first flow path, 3B second flow path, 4, 5, 6 connecting member, 4a, 5a, 6a recess, 4b, 5b, 6b flange, 7 first flow guide, 7A first inclined surface, 7B second inclined surface, 8 second flow guide, 8A third inclined surface, 8B fourth inclined surface, 9A first opening, 9B second opening, 10 heat Exchanger, 11 collar unit, 30 heat source circuit, 31 compressor, 32 outdoor heat exchanger, 33 expansion valve, 34 switch, 35 blower, 39 pipe, 40 use circuit, 41 pump, 43 blower, 49 pipe, 50 intermediate Heat exchanger, 60 control units, 100 air conditioners.

Claims (10)

A fin laminate in which a plurality of fins are laminated in a first direction at intervals;
A first flow path through which the fluid flows through the plurality of fins;
A connection member having a recess, wherein a periphery of an opening of the recess is fixed to an end of the fin laminate in the first direction.
A heat exchanger in which the recess covers the first opening of the first flow passage, and the fluid flowing into the recess from the first opening flows in the recess in a second direction intersecting with the first direction; And
A first flow guide having a first inclined surface is provided beside the first opening on the side of the second direction, the distance in the second direction increasing with distance from the first opening in the first direction. ,
The first inclined surface has a groove extending from the first opening in the second direction,
Heat exchanger. A fin laminate in which a plurality of fins are laminated in a first direction at intervals;
A first flow path through which the fluid flows through the plurality of fins;
A connection member having a recess, wherein a periphery of an opening of the recess is fixed to an end of the fin laminate in the first direction.
A heat exchanger in which the recess covers the first opening of the first flow passage, and the fluid flowing into the recess from the first opening flows in the recess in a second direction intersecting with the first direction; And
A first flow guide having a first inclined surface is provided beside the first opening on the side of the second direction, the distance in the second direction increasing as the distance from the first opening in the first direction increases. ,
A second inclined side, which is inclined with respect to the first direction and is opposed to the first inclined surface of the first flow guide, on a side of the first opening opposite to the first flow guide. Equipped with a flow guide,
Heat exchanger. A second flow path through which the fluid flows through the plurality of fins,
The recess covers the second opening of the second flow path, and the heat flowing into the recess from the first opening flows in the second direction in the recess and flows out of the second opening. An exchanger,
The first flow guide is provided on a side of the second opening on the side of the first opening, and a second slope in which a distance from the second opening to the first opening increases as the distance from the second opening in the first direction increases. Having a surface,
The heat exchanger according to claim 1 or 2. The heat exchanger according to claim 3 , wherein the first inclined surface and the second inclined surface of the first flow guide are configured as a continuous surface. The heat exchanger according to any one of claims 1 to 4, wherein the first flow guide is fixed to an end of the fin laminate. The heat exchanger according to any one of claims 1 to 4, wherein the first flow guide is a convex portion protruding toward the concave side of the plate at the end of the fin laminate. When a third direction intersects the first direction and is perpendicular to the second direction,
The heat exchanger according to any one of the third direction of the first inclined surface width claims 1 greater than the width of the first opening 6. The heat exchanger according to any one of claims 1 to 7 , wherein the first flow path is configured by connecting a collar portion of a fin. A fin laminate in which a plurality of fins are laminated in the first direction at intervals;
A first flow path through which the fluid flows through the plurality of fins;
A connection member having a recess, wherein a periphery of an opening of the recess is fixed to an end of the fin laminate in the first direction.
A heat exchanger in which the recess covers the first opening of the first flow passage, and the fluid flowing into the recess from the first opening flows in the recess in a second direction intersecting with the first direction; And
A first flow guide having a first inclined surface is provided beside the first opening on the side of the second direction, the distance in the second direction increasing with distance from the first opening in the first direction. ,
The first flow path is constituted by a tube or a connected collar portion,
The first flow guide comprises at least a portion of the collar or the tube protruding into the recess;
Heat exchanger. A heat exchanger according to any one of claims 1 to 9 ,
A utilization circuit for supplying a fluid to the heat exchanger,
A heat source for heating or cooling the fluid.
Air conditioner.

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