stacking collector, heat exchanger, and air conditioning unit

专利摘要:
STACKING TYPE COLLECTOR, HEAT EXCHANGER, AND AIR CONDITIONING DEVICE. A stack type collector (2) according to the present invention includes: a first plate-shaped unit (11) having a plurality of first discharge flow passages (11A) formed therein; and a second plate-shaped unit (12) mounted on the first plate-shaped unit (11), the second plate-shaped unit (12) having a distribution flow passage (12A) formed therein, the passage distribution flow (12A) being configured for refrigerant distribution, which passes through a first inlet flow passage (12a) to flow into the second plate-shaped unit (12), for the plurality of first flow passages discharge flow (11A) to drain refrigerant from the second plate-shaped unit (12), in which the distribution flow passage (12A) includes a branched flow passage (12b) including: an opening orifice; a first straight part parallel to a direction of gravity, the first straight part having a lower end communicating with the opening orifice through a first connecting part; and a second rectilinear part parallel to the gravity direction, (...).
公开号:BR112015028496B1
申请号:R112015028496-5
申请日:2014-05-13
公开日:2021-02-09
发明作者:Takuya Matsuda；Akira Ishibashi；Takashi Okazaki；Shigeyoshi MATSUI；Shinya Higashiiue；Daisuke Ito；Atsushi Mochizuki
申请人:Mitsubishi Electric Corporation；
IPC主号:

专利说明:

Field
[001] The present invention relates to a stack type collector, a heat exchanger and an air-conditioning device. Description of the Prior Art
[002] As a stacking collector of the related technique, a stacking collector is known including a first plate-shaped unit having a plurality of discharge flow passages formed therein, and a second plate-shaped unit stacked on top of the plate. first plate-shaped unit and having a distribution flow passage formed thereon, for refrigerant distribution, which passes through an intake flow passage to flow into the second plate-shaped unit, for the plurality of passages of discharge flow formed in the first plate-shaped unit to cause the refrigerant to drain from the second plate-shaped unit. The dispensing flow passage includes a branched flow passage having a plurality of grooves extending perpendicular to a refrigerant inlet flow direction. The refrigerant passing through the intake flow passage to flow into the branched flow passage passes through the plurality of grooves to be branched and a plurality of flows to thereby pass through the plurality of discharge flow passages formed in the first plate-shaped unit to flow from the first plate-shaped unit (for example, see Patent Literature 1). List of Citations Patent Literature
[003] Patent Literature 1: Unexamined patent application JP 2000 / 161.818 (paragraph] 0012] up to paragraph [0020], figure 1, figure 2) Summary of the Invention Technical problem
[004] In said stacking type collector, when it is sweated in a state in which the flow direction of the refrigerant flowed into the branched flow passage is not parallel to the direction of gravity, the refrigerant can be affected by gravity to cause a deficiency or excess of the refrigerant in either of the branching directions. In other words, the stacking collector of the related technique has a problem because the uniformity in the distribution of the refrigerant is low.
[005] The present invention was made in view of the aforementioned problems, and aims to provide an improved stacking type collector in terms of uniformity in the distribution of refrigerant. In addition, the present invention aims to provide an air conditioner device improved in uniformity in the distribution of refrigerant. Solution of the problem
[006] In accordance with an embodiment of the present invention, a stack type collector is provided which includes: a first plate-shaped unit having a plurality of first discharge flow passages formed therein; and a second plate-shaped unit being mounted on the first plate-shaped unit, the second plate-shaped unit having a distribution flow passage formed therein, the distribution flow passage being configured to distribute refrigerant, which passes through a first intake flow passage to flow to the second plate-shaped unit, for the plurality of first discharge flow passages to cause the refrigerant to flow from the second plate-shaped unit, in which the passage distribution flow includes a branched flow passage including: an opening orifice; a first rectilinear particle parallel to a direction of gravity, the first rectilinear part having a lower end communicating with the opening orifice through a first connecting part; and a second rectilinear part parallel to the direction of gravity, the second rectilinear part having an upper end communicating with the opening hole through a second connection part, in which at least a part of the first connection part and at least a part of the second connection part are not parallel to the direction of gravity, and in which the refrigerant flows into the branched flow passage through the opening orifice, passes through each of the first connection part and the second connection part to flow to within each a lower end of the first straight line and the upper end of the second straight line, and it flows from the branched flow passage through each of the upper end of the first straight line and a lower end of the second straight line. Advantageous effects of invention
[007] In the stack type manifold according to a modality of the present invention, the distribution flow passage includes the branched flow passage including the opening orifice, the first straight part the first straight part parallel to the direction of gravity, the first rectilinear part having the lower end communicating with the opening orifice through the first connection part, and the second rectilinear part parallel to the direction of gravity, the second rectilinear part having the upper end communicating with the opening orifice through the second part of connection. At least the part of the first connection part and at least the part of the second connection part are formed to be parallel to the direction of gravity. The refrigerant flows into the branched flow passage through the opening orifice, passes through each of the first connection part and second connection part to flow into each of the lower end of the first rectilinear part and the upper end of the second straight portion, and flows from the branched flow passage through each of the upper end of the first straight portion and the lower end of the second straight portion. Consequently, the flow of the refrigerant in a direction perpendicular to the direction of gravity is uniformized in the first rectilinear part and in the second rectilinear part, which are parallel to the direction of gravity, and then the refrigerant flows out of the branched flow passage, which reduces the influence of gravity and increases the uniformity in the distribution of the refrigerant. Brief Description of Drawings
[008] Figure 1 is a view illustrating a configuration of a heat exchanger according to Mode 1.
[009] Figure 2 is a perspective view illustrating the heat exchanger according to Mode 1, in a state in which a stack type collector is disassembled.
[0010] Figure 3 is a developed view of the stacking collector of the heat exchanger according to Mode 1.
[0011] Figure 4 is a developed view of the stacking collector of the heat exchanger according to Mode 1.
[0012] Figure 5 is a view illustrating a modified example of a flow passage formed in a third plate-shaped member of the heat exchanger according to Mode 1.
[0013] Figure 6 is a view illustrating a modified example of a flow passage formed in a third plate-shaped member of the heat exchanger according to Mode 1.
[0014] Figure 7 is a perspective view illustrating the heat exchanger according to Mode 1 in a state in which the stacking type collector is disassembled.
[0015] Figure 8 is a developed view of the stacking collector of the heat exchanger according to Mode 1.
[0016] Figure 9 is a view illustrating the flow passage formed in the third plate-shaped member of the heat exchanger according to Mode 1.
[0017] Figure 10 is a view illustrating the flow passage formed in the third plate-shaped member of the heat exchanger according to Mode 1.
[0018] Figure 11 is a graph showing a relationship between a rectilinear ratio of each of the first rectilinear part and a second rectilinear part and a distribution ratio in the flow passage formed in the third plate-shaped member of the heat exchanger. according to Modality 1.
[0019] Figure 12 is a graph showing a relationship between a rectilinear ratio of each of the first rectilinear part and a second rectilinear part and an AK value of the heat exchanger in the flow passage formed in the third plate-shaped member of the exchanger heat according to Mode 1.
[0020] Figure 13 is a graph showing a relationship between a rectilinear ratio of each of the first rectilinear part and a second rectilinear part and an AK value of the heat exchanger in the flow passage formed in the third plate-shaped member of the exchanger heat according to Mode 1.
[0021] Figure 14 is a graph showing a relationship between a rectilinear ratio of a third rectilinear part and a distribution ratio in the flow passage formed in the third plate-shaped member of the heat exchanger according to Mode 1.
[0022] Figure 15 is a graph showing a relationship between a bending angle of a connection part and a distribution ratio in the flow passage formed in the third plate-shaped member of the heat exchanger according to Mode 1.
[0023] Figure 16 is a diagram illustrating a configuration of an approximately, air conditioner to which the heat exchanger according to Mode 1 is applied.
[0024] Figure 17 is a perspective view of a Modified Example-1 of the heat exchanger according to Mode 1 in a state in which the stacking collector is disassembled.
[0025] Figure 19 is a perspective view of a Modified Example-2 of the heat exchanger according to Mode 1 in a state in which the stacking collector is disassembled.
[0026] Figure 20 is a perspective view of a Modified Example-3 of the heat exchanger according to Mode 1 in a state in which the stacking collector is disassembled.
[0027] Figure 21 is a developed view of the stacking collector of Modified Example-3 of the heat exchanger according to Mode 1.
[0028] Figure 22 is a perspective view of Example-4 Modified of the heat exchanger according to Mode 1 in a state in which the stacking collector is disassembled.
[0029] Figure 23 is a perspective view of the main part of Example-5 Modified of the heat exchanger according to Modality 1 in a state in which the stacking collector is disassembled.
[0030] Figure 24 is a sectional view of the main part of Example-5 Modified of the heat exchanger according to Mode 1 in a state in which the stacking collector is disassembled.
[0031] Figure 25 is a perspective view of the main part of Example-6 Modified of the heat exchanger according to Modality 1 in a state in which the stacking collector is disassembled.
[0032] Figure 26 is a sectional view of the main part of Modified Example-6 of the heat exchanger according to Mode 1 in a state in which the stacking collector is disassembled.
[0033] Figure 27 is a perspective view of the Modified Example-7 of the heat exchanger according to Mode 1 in a state in which the stack type collector is disassembled.
[0034] Figure 28 is a view illustrating a configuration of a heat exchanger according to Mode 2.
[0035] Figure 29 is a perspective view illustrating the heat exchanger according to Mode 2 in a state in which a stacking collector of the heat exchanger is disassembled.
[0036] Figure 30 is a developed view of the stacking collector of the heat exchanger according to Mode 2.
[0037] Figure 31 is a diagram illustrating a configuration of an approximately, air conditioner to which the heat exchanger according to Mode 2 is applied.
[0038] Figure 32 is a view illustrating a configuration of a heat exchanger according to Mode 3.
[0039] Figure 33 is a perspective view illustrating the heat exchanger according to Modality 3 in a state in which the stack type collector is disassembled.
[0040] Figure 34 is a developed view of the stacking collector of the heat exchanger according to Mode 3.
[0041] Figure 35 is a diagram illustrating a configuration of the air conditioning unit to which the heat exchanger according to Mode 3 is applied. Description of Modalities
[0042] Now, a stack type collector according to the present invention is described with reference to the drawings.
[0043] Note that, below, a case is described in which the stacking collector according to the present invention distributes refrigerant flowing into a heat exchanger, but the stacking collector according to the present invention can distribute refrigerant flowing to other devices. In addition, the configuration, operation and other matters described below are merely examples, and the present invention is not limited to such configuration, operation and other matters. In addition, in the drawings, the same or similar components are denoted by the same reference symbols, or the symbols for them are omitted. Mode 1
[0044] A heat exchanger according to Mode 1 is described. <Heat exchanger configuration>
[0045] Now, the configuration of the heat exchanger according to Mode 1 will be described.
[0046] Figure 1 is a view illustrating the configuration of the heat exchanger according to Mode 1.
[0047] As illustrated in figure 1, a heat exchanger 1 includes a stack type collector 2, a collector 3, a plurality of first heat transfer tubes 4, a retaining member 5 and a plurality of fins 6.
[0048] The stack 2 collector includes a refrigerant inlet flow port 2A and a plurality of refrigerant outlet flow ports 2B. The manifold 3 includes a plurality of refrigerant inlet flow ports 3A and a refrigerant outlet flow port 3B. Refrigerant tubes are connected to the refrigerant inlet flow port 2A of the stack type collector 2 and the refrigerant outlet flow port 3B of the collector 3. The plurality of first heat transfer tubes 4 are connected between the plurality of holes refrigerant outlet flow rate 2B from the stack type collector 2 and the plurality of refrigerant inlet flow ports 3A from the collector 3.
[0049] The first heat transfer tube 4 is a flat tube having a plurality of flow passages therein. The first heat transfer tube 4 is made, for example, from aluminum. Final portions of the plurality of first heat transfer tubes on the side of the stack-type collector 2 in a state in which the final portions are retained by the plate-like retaining member 5. The retaining member 5 is laid, for example, aluminum. The plurality of fins 6 are attached to the first heat transfer tubes 4. The fin 6 is made, for example, of aluminum. It is preferred that the first heat transfer tubes 4 and fins 6 are joined by brazing. Note that, in figure 1, a case is illustrated in which eight first heat transfer tubes 4 are provided, but the present invention is not limited to this case. <Coolant flow in the heat exchanger>
[0050] Now, the flow of refrigerant in the heat exchanger according to Mode 1 is described.
[0051] The refrigerant flowing through the refrigerant pipe passes through the refrigerant inlet flow port 2A to flow into the stack-type manifold 2 to be distributed, and then passes through the plurality of refrigerant outlet flow ports 2B to flow out to the plurality of first heat transfer tubes 4. In the plurality of first heat transfer tubes 4, the refrigerant exchanges heat with air supplied by a fan, for example. The refrigerant flowing through the plurality of first heat transfer tubes 4 passes through the plurality of refrigerant inlet flow ports 3A to flow into the collector 3 to be joined and then passes through the outlet flow port of refrigerant 3B to flow towards the refrigerant pipe. The refrigerant can flow inversely. <Laminated collector configuration>
[0052] Now, the stacking collector configuration of the heat exchanger according to Mode 1 will be described.
[0053] Figure 2 is a perspective view of the heat exchanger according to Mode 1 in a state in which the stacking collector is disassembled.
[0054] As shown in figure 2, the stack type collector 2 includes a single plate-shaped unit 11 and a second plate-shaped unit 12. The first plate-shaped unit 11 and the second plate-shaped unit 12 are stacked on top of each other.
[0055] The first plate-shaped unit 11 is stacked on the flow side of the refrigerant outlet. The first plate-shaped unit 11 has a plurality of first discharge flow passages 11A formed therein. The plurality of first discharge flow passages 11A corresponds to the plurality of refrigerant outlet flow ports 2B in Figure 1.
[0056] The first plate-like member 21 has a plurality of flow passages 21A formed therein. Each passage of the plurality of flow passages 21A is a through hole having an internal peripheral surface shaped in conformation with an external peripheral surface of the first heat transfer tube 4. When the first plate-shaped member 21 is stacked, the plurality of flow passages 21A function as the plurality of first discharge flow passages 11A. The first plate-shaped member 21 has a thickness of about 1mm to 10mm, and is made of aluminum, for example. When the plurality of flow passages 21A are formed by pressing or other processing, the work is simplified, and manufacturing is reduced in cost.
[0057] The final portions of the first heat transfer tubes 4 are projected from the surface of the retaining member 5. When the first plate-shaped unit 11 is stacked on the retaining member so that the inner peripheral surfaces of the first heat passages discharge flow 11A are adjusted to the outer peripheral surfaces of the respective end portions of the first heat transfer tubes 4, the first heat transfer tubes 4 are connected to the first discharge flow passages 11A. The first discharge flow passages 11A and the first heat transfer tubes 4 can be positioned by, for example, adjusting between a convex portion formed in the retaining member 5 and a concave portion formed in the first plate-shaped unit 11 In this case, the final portions of the first heat transfer tubes 4 can protrude from the surface of the retaining member 5. The retaining member 5 can be omitted, so that the first heat transfer tubes 4 are directly connected to the first discharge flow passages 11A. In this case, cost and similar components are reduced.
[0058] The second plate-shaped unit 12 is stacked on the flow side of the refrigerant inlet. The second plate-shaped unit 12 includes a second plate-shaped member 22 and a plurality of third plate-shaped members 23_1a 23_3. The second plate-shaped unit 12 has a distribution flow passage 12A formed therein. The delivery flow passage 12A includes a first intake flow passage 12a and a plurality of branched flow passages 12b. The first inlet flow passage 12a corresponds to the refrigerant inlet flow port 2A in figure 1.
[0059] The second plate-like member 22 has a flow passage 22A formed therein. The flow passage 22A is a circular through hole. When the second plate-shaped member 22 is stacked, the flow passage 22A functions as the first inlet flow passage 12a. The second plate-shaped member 22 has a thickness of about 1 mm to 10 mm, and is made of aluminum, for example. When flow passage 22A is formed by pressing work or other processing, the work is simplified and the cost of manufacture and the like is reduced.
[0060] For example, an accessory or other components of this type is provided on the surface of the second plate-shaped member 22 on the refrigerant inlet flow side, and the refrigerant tube is connected to the first inlet flow passage 12a through the accessory or other component of this type. The inner peripheral surface of the first intake flow passage 12a can be shaped to fit the outer peripheral surface of the refrigerant pipe, so that the refrigerant pipe can be directly connected to the first intake flow passage 12a without using the attachment or other component of the type. In this case, the cost component and the like are reduced.
[0061] The plurality of third member in plate form 23_1 to 23_3 have, respectively, a plurality of flow passages 23A_1 to 23A_3 formed therein. The plurality of flow passages 23A_1 through 23A_3 each constitute a through-pass groove. The form of the through slot is described in detail below. When a plurality of third plate-like members 23_1 to 23_3 are stacked, each of the plurality of flow passages 23A_1 to 23A_3 functions as a branched flow pass 12b. The plurality of third plate-shaped members 23_1 to 23_2 each have a thickness of about 1 mm to 10 mm, and are made of aluminum, for example. When the plurality of flow passages 23A_1 to 23A_3 is formed by pressing work or other processing, the work is simplified and the cost of manufacture and the like is reduced.
[0062] In the following, in some cases, the plurality of third plate-shaped members 23_1 to 23_3 is collectively referred to as the third plate-shaped member 23. Next, in some cases, the plurality of flow passages 23A_1 a 23A_3 is collectively referred to as flow passage 23A. Next, in some cases, the retaining member 5, the first plate-shaped member 21, the second plate-shaped member 22, and the third plate-shaped member 23 are collectively referred to as the shaped member of plate.
[0063] The branched flow passage 12 sprays the refrigerant by flowing through it in two flows to cause the refrigerant to flow through them. Therefore, when the number of first heat transfer tubes 4 to be connected is eight, at least three third plate members 23 are required. When the number of first heat transfer tubes 4 to be connected is sixteen, at least 4 third plate-like members 23 will be required. The number of first heat transfer tubes 4 to be connected is not limited to powers of 2. In this case, the branched flow passage 12b and the unbranched flow passage can be combined with each other. Note that the number of the first heat transfer tubes 4 to be connected can be two.
[0064] Figure 3 is a developed view of the stacking collector of the heat exchanger according to Mode 1.
[0065] As illustrated in figure 3, the flow passage 23A secured in the third plate-shaped member 23 has a shape in which a lower end 23c of a first straight portion 23a and an upper end 23f of a second straight portion 23d are connected to each other through a third straight portion 23g. The first straight portion 23a and the second straight portion 23d are parallel to the direction of gravity. The third straight portion 23g is perpendicular to the direction of gravity. The third straight portion 23g can be tilted from a state perpendicular to the direction of gravity. The branched flow passage 12b is secured by the closure, by an adjacent stacked member on the refrigerant inlet flow side, the flow passage 23A in another region Swg p «q woc tgik« q rctekcn 45j * cfkcnVg tefetkfc eqoq “orifice fg cdertwtc ”45j” + entte woc rqt> «q fincn 45j and woc rqt>« q fincn 45k fc teteektc rctte straight 23g, and closing, by an adjacent stacked member on the refrigerant discharge flow side, the flow passage 23A in a region other than an upper end 23b of the first straight portion 23a and a lower end 23e of the second straight portion 23d.
[0066] In order to branch the refrigerant by flowing pear into the flow passage 23A to have different heights and to cause the refrigerant to drain from it, the upper end 23b of the first rectilinear part 23a is positioned on the upper side in relation to the orifice opening 23j, and the lower end 23e of the second rectilinear part 23d is positioned on the lower side in relation to the opening orifice 23j. In particular, when a length of the first straight portion 23a and a length of the second straight portion 23d are substantially equal to each other, and the opening hole 23j is positioned substantially in the center between the lower end 23c of the first straight portion 23a and the end upper 23f of the second straight line 23dm each distance from the opening orifice 23j along the flow passage 23A to each of the upper end 23b of the first straight line 23a and the lower end 23e of the second straight line 23d can be less pressed without complicating the form. When the straight connection between the upper end 23b of the first straight portion 23a and the lower end 23e of the second straight portion 23d is adjusted parallel to the longitudinal direction of the third plate-like member 23, the dimension of the third plate-like member 23 in the transverse direction it can be decreased, which reduces the cost component, the weight etc. In addition, when the straight connection between the upper end 23b of the first straight portion 23a and the lower end 23e of the second straight portion 23d is adjusted parallel to the arrangement direction of the first heat transfer tubes 4, space savings can be obtained in the heat exchanger 1.
[0067] Figure 4 is a developed view of the stacking collector of the heat exchanger according to Mode 1.
[0068] As illustrated in figure 4, when the arrangement direction of the first heat transfer tubes 4 is not parallel to the direction of gravity, in other words, when the arrangement direction intersects the direction of gravity, the third straight part 23g it will not be perpendicular to the longitudinal direction of the third plate-like member 23. In other words, the stack-type collector 2 is not limited to a stack-type collector in which the plurality of first discharge flow passages 11A are arranged along the direction gravity, and can be used in a case where the heat exchanger 1 is installed in an inclined manner, such as a heat exchanger for an indoor unit of a wall-mounted ambient air conditioner, an external unit for an appliance air conditioner, or an external refrigerator unit. Note that, in figure 4, the case is illustrated in which the longitudinal direction of the cross section of the flow passage 21A formed in the first plate-shaped member 21, in other words, the longitudinal direction of the cross section of the first flow passage of 21A. outlet 11A is perpendicular to the longitudinal direction of the first plate-shaped member 21, but the longitudinal direction of the cross section of the first outlet flow passage 11A may be perpendicular to the direction of gravity.
[0069] The flow passage 23A includes connection parts 23k and 23l to connect each of the end portion 23h and end portion 23j of the third straight portion 23g to each of the lower end 23c of the first straight portion 23a and the upper end 23f of the second rectilinear part 23d. The connecting parts 23k and 23l can each be a straight line or a curved line. At least a part of the connecting part 23k and at least a part of the connecting part 23l are not parallel to the direction of gravity. The connecting part 23k to connect the end portion 23h of the third straight part 23g and the lower end 23c of the first straight part 23a eqttgurqpfg c woc “rtkogktc rctVg fg eqpgz« q ”fc rtgugpVg kpxgp>« qo C rctVg of connection 23l to connect the final portion 21i of the third rectilinear part 23g and the upper end 23f of the second rectilinear part 23d corresponds to woc “ugiwpfc rartg fg eqpgz« q ”fc rtgugptg kpxgp>« qo
[0070] The flow passage 23A can be formed as a through-groove shaped so that the connecting parts 23k and 23l are branched, and other flow passages can communicate with the branched flow passage 12b. When other flow passages do not communicate with the branched flow passage 12b, uniformity in the distribution of the refrigerant is reliably increased.
[0071] Figures 5 and 6 are seen illustrating, each one, a modified example of the flow passage formed in the third plate-shaped member of the heat exchanger according to Mode 1.
[0072] As illustrated in figure 5, the flow passage may not include the third straight portion 23g. In other words, a final portion of the connecting portion 23k on a non-continuous side to the lower end 23c of the first straight portion 23a and a final portion of the connecting portion 23l on a non-continuous side to the upper end 23f of the second straight portion 23d may each be directly continuous with the opening orifice 23j. In addition, a final portion of the connecting portion 23k on a continuous side to the opening orifice 23j and a final portion of the connecting portion 23l on a continuous side to the opening orifice 23j may not each be perpendicular to the direction of gravity . Even without the third straight portion 23g, the flow passage 23A includes the first straight portion 23a and the second straight portion 23d, so that the uniformity in distribution of the refrigerant can be increased. When the flow passage 23A includes the third straight portion 23g, the uniformity in the distribution of the refrigerant is further enhanced.
[0073] As shown in figure 6, for example, when the arrangement direction of the first heat transfer tubes 4 intersects the direction of gravity, the flow passage 23A may have a configuration in which the lower end 23c of the first rectilinear part 23a is positioned closer to the final portion 23h of the ror 23g, and the upper end 23f of the second straight portion 23d is positioned closer to the final portion 23i of the third straight portion 23g. <Refrigerant flow in laminated collector>
[0074] Now, the flow of refrigerant in the stacker-type collector of the heat exchanger according to Mode 1 is described.
[0075] As shown in figures 3 and 4, the refrigerant passing through the flow passage 22A of the second plate-shaped member 22 flows into the opening orifice 23j of the flow passage 23A formed in the third plate-shaped member 23_1 . The refrigerant flowing into the opening orifice 23j impacts against the surface of the stacked member adjacent to the third plate-shaped member 23_1, and is branched in two flows, respectively, towards the final portion 23h and the final portion 23i of the third portion straight 23g. The branched refrigerant passes through each of the connecting parts 23k and 23l of the flow passage 23A to flow into each of the lower end 23c of the first straight portion 23a and the upper end 23f of the second straight portion 23d of the flow passage 23A. Then, the branched refrigerant reaches each of the upper end 23b of the first straight portion 23g and the lower end 23e of the second straight portion 23d of the flow passage 23A and flows into the opening orifice 23j of the flow passage 23A formed in the third member in the form of a plate 23_2.
[0076] Similarly, refrigerant flowing into the opening orifice 23j of the flow passage 23A formed in the third plate-shaped member 23_2 impacts against the surface of the stacked member adjacent to the third plate-shaped member 23_2, and is branched in two flows, respectively, towards the final portion 23h and the final portion 23i of the third rectilinear portion 23g. The branched refrigerant passes through each of the connecting parts 23k and 23l of the flow passage 23A to flow into each of the lower end 23c of the first straight portion 23a and the upper end 23f of the second straight portion 23d of the flow passage 23A. Then, the branched refrigerant reaches each of the upper end 23b of the first straight portion 23a and the lower end 23e of the second straight portion 23d of the flow passage 23A and flows into the opening orifice 23j of the flow passage 23A formed in the third member in the form of a plate 23_3.
[0077] Similarly, refrigerant flowing into the opening orifice 23j of the flow passage 23A formed in the third plate-shaped member 23_3 impacts against the surface of the stacked member adjacent to the third plate-shaped member 23_3, and is branched in two flows, respectively, towards the final portion 23h and the final portion 23i of the third rectilinear portion 23g. The branched refrigerant passes through each of the connecting parts 23k and 23l of the flow passage 23A to flow into each of the lower end 23c of the first straight portion 23a and the upper end 23f of the second straight portion 23d of the flow passage 23A. Then, the branched refrigerant reaches each of the upper end 23b of the first straight portion 23a and the lower end 23e of the second straight portion 23d of the flow passage 23A and passes through the flow passage 21A of the first plate-shaped member 21 to flow into the first heat transfer tube 4. <Method of laminating plate-shaped members>
[0078] Now, a method of stacking the respective plate-shaped collector-type members of the heat exchanger according to Mode 1 is described.
[0079] The respective plate-shaped members can be stacked by brazing. A capping member on both sides having a laminated weld material on both of its surfaces can be used for all alternating plate-shaped members or plate-shaped members to supply the brazing material for the joint. A one-sided capping member, having a brazing solder material laminated to its surface, can be used for all plate-shaped members to supply the brazing solder material for the joint. A sheet of brazing material can be stacked between the respective members in the form of a plate to supply the brazing material. A paste solder material can be applied between the respective plate-shaped members to supply the solder material. A capping member on both sides having a brazing weld material laminated on both of its surfaces can be stacked between the respective plate-shaped members to supply the brazing material.
[0080] Through rolling with the use of strong solder, the plate-shaped members are stacked without a gap between them, which suppresses leakage of the refrigerant and ensures even more resistance to pressure. When the plate-shaped members are pressurized during welding, the occurrence of welding failure is further suppressed. When processing is carried out that promotes the formation of a fillet, such as the formation of a rib in a position in which leakage of the refrigerant is capable of occurring, the occurrence of brazing failure is further suppressed.
[0081] In addition, when all members to be subjected to brazing, including the first heat transfer tube 4 and fin 6, are made of the same material (for example, made of aluminum), the members can be collectively subject to strong welding, which increases productivity. After welding on the stacking collector 2 is performed, the strong welding of the first heat transfer tube 4 and the fin 6 can be performed. In addition, only the first plate-shaped unit 11 can be joined first to the retaining member 5 by brazing, and the second plate-shaped unit 12 can be joined by brazing afterwards.
[0082] Figure 7 is a perspective view of the heat exchanger according to Mode 1 in a state in which the stacking collector is disassembled. Figure 8 is a developed view of the stacking collector of the heat exchanger according to mode 1.
[0083] In particular, a plate-shaped member having a strong welding material laminated on both sides, in other words, a capping member on both sides can be stacked between the respective plate-shaped members to supply the strong welding material. As illustrated in figures 7 and 8, a plurality of capping members on both sides 24_1 to 24_5 is stacked between the respective plate-shaped members. In what follows, in some cases, the plurality of capping members on both sides 24_1 through 24_5 is collectively referred to as the capping member on both sides 24. Note that the capping member on both sides 24 can be stacked between a portion of the plate-like members, and a brazing material can be supplied between the remaining plate-like members by other methods.
[0084] The capping member on both sides 24 has a flow passage 24A, which passes through the capping member on both sides 24, formed in a region opposite a refrigerant outlet flow region of the flow passage formed in the adjacent stacked plate-shaped member on the refrigerant inlet flow side. The flow passage 24A formed in the capping member on both sides 24 stacked between the second plate-shaped member 22 and the third plate-shaped member 23 is a circular through hole. The flow passage 24A formed in the capping member on both sides 24_5 stacked between the first plate-shaped member 21 and the retaining member 5 is a through hole having an inner peripheral surface shaped in accordance with the outer peripheral surface of the first heat transfer tube 4.
[0085] When the capping member on both sides 24 is stacked, the flow passage 24A functions as a refrigerant partition flow passage for the first discharge flow passage 11A and the distribution flow passage 12A. In a state in which the capping member on both sides 24_5 is stacked on top of the retaining member 5, the final portions of the first heat transfer tubes 4 may or may not project from the surface of the capping member on both sides 24_5 . When flow passage 24A is formed by pressing work or other processing, the work is simplified, and the cost of manufacture and the like is reduced. When all members to be subjected to brazing, including the capping member on both sides 24, are made of the same material (for example, made of aluminum), the members can be collectively subjected to hard soldering, which increases the productivity.
[0086] By the formation of the refrigerant partition flow passage by the capping member on both sides 24, in particular, branched flows of refrigerant flowing from the branched flow passage 12b can be reliably partitioned from one another. In addition, by the amount of thickness of each capping member on both sides 24, an inlet length for refrigerant flowing into the branched flow passage 12b or the first discharge flow passage 11A can be ensured, which increases the uniformity in the distribution of refrigerant. In addition, the refrigerant flows can be reliably partitioned from one another and, thus, the degree of freedom in the design of the branched flow passage 12b can be increased. <Flow way of the third member in the form of a plate>
[0087] Figures 9 and 10 are seen illustrating, each, the flow passage formed in the third plate-shaped member of the heat exchanger according to Modality 1. Note that, in figures 9 and 10, a part of the flow passage formed in a stacked member adjacent to the third plate-shaped member is indicated by the dotted lines. Figure 9 illustrates the flow passage 23A formed in the third plate-shaped member 23 in a state in which the capping member on both sides 24 is not stacked (state of figures 2 and 3), and figure 10 illustrates the flow passage 23A formed on the third plate-shaped member 23 in a state in which the capping member on both sides 24 is stacked (state of figures 7 and 8).
[0088] As illustrated in figures 9 and 10, the center of the refrigerant outlet flow region of the first straight portion 23a of flow passage 23A is defined as the upper end 23b of the first straight portion 23a, and a distance between the end upper 23b and the lower end 23c of the first straight line 23a is defined as a straight line distance L1. In addition, the center of the refrigerant outlet flow region of the second straight portion 23d of flow passage 23A is defined as the lower end 23e of the second straight portion 23d, and a distance between the lower end 23e and the upper end 23f of the second rectilinear part 23d is defined as a straight L2 distance. In addition, an equivalent hydraulic diameter of the first straight portion 23a is defined as an equivalent hydraulic diameter De1, and a ratio of the straight distance L1 and the equivalent hydraulic diameter De1 is defined as a straight ratio L1 / De1. In addition, an equivalent hydraulic diameter of the second straight portion 23d is defined as an equivalent hydraulic diameter De2, and a ratio of the straight distance L2 and the equivalent hydraulic diameter De2 is defined as a straight ratio L2 / De2. A ratio of a flow of the refrigerant flowing from the upper end 23b of the first straight portion 23a of the flow passage 23A and a sum of a flow of the refrigerant flowing from the upper end 23b of the first straight portion 23a of the flow passage 23c of the second straight portion 23d of the flow passage 23A is defined as a distribution ratio R.
[0089] Figure 11 is a graph showing a relationship between the rectilinear ratio of each of the first rectilinear part and the second rectilinear part, and the distribution ratio in the flow passage formed in the third plate-shaped member of the heat exchanger according to with Mode 1. Note that figure 11 shows a change in the distribution ratio R in the subsequent flow passage 23A to which the refrigerant flows from the previous flow passage 23A when the straight ratio L1 / De1 (= L2 / De2) of the previous flow passage 23A is changed into a state in which the L1 / De1 rectilinear ratio is set equal to the L2 / De2 rectilinear ratio.
[0090] As shown in figure 11, the distribution ratio R is changed so that the distribution ratio R is increased until the L1 / De1 rectilinear ratio and the L2 / De2 rectilinear ratio reach 10.0, and the distribution ratio R reaches 0.5 when the L1 / De1 rectilinear ratio and the L2 / De2 rectilinear ratio are 10.0 or greater. When the L1 / De1 rectilinear ratio and the L2 / De2 rectilinear ratio are less than 10.0 due to the connection parts 23k and 23l not being parallel to the direction of gravity, the refrigerant flows into the third straight part 23g of the flow passage subsequent 23A in a state of causing deviation and thus the distribution ratio R does not reach 0.5.
[0091] Figures 12 and 13 are graphs showing a relationship between the rectilinear ratio of each of the first rectilinear and second rectilinear part and an AK value of the heat exchanger in the flow passage formed in the third plate-shaped member of the exchanger of heat according to Mode 1. Note that figure 12 shows a change in the AK value of heat exchanger 1 when the L1 / De1 rectilinear ratio (= L2 / De2) is changed. Figure 13 shows a change in the effective AK value of heat exchanger 1 when the straight L1 / De1 ratio (= L2 / De2) is changed. The AK value is a multiplication value of a heat transfer area A [m2] of heat exchanger 1 and a general heat transfer coefficient K [L / (S.m2.K)] of heat exchanger 1, and the effective AK value is a value defined based on a multiplication value of the AK value and the aforementioned R distribution ratio. Once the AK value is higher, the performance of heat exchanger 1 is improved.
[0092] On the other hand, as shown in figure 12, as the L1 / De1 rectilinear ratio and the L2 / De2 rectilinear ratio are greater, an arrangement interval of the first heat transfer tubes 4 is increased, in other words, the the number of the first heat transfer tubes 4 is reduced and thus the AK value of the heat exchanger is reduced. Therefore, as shown in figure 13, the effective AK value is changed so that the effective AK value is increased until the L1 / De1 rectilinear ratio and the L2 / De2 rectilinear ratio reach 3.0, and the effective AK value is decreased while reducing a decreasing amount when the L1 / De1 rectilinear ratio and the L2 / De2 rectilinear ratio is 3.0 or greater. That is, when the L1 / De1 rectilinear ratio and the L2 / De2 rectilinear ratio are adjusted to 3.0 or more, the effective AK value, in other words, the performance of heat exchanger 1 can be maintained.
[0093] As illustrated in figures 9 and 10, a distance between the center of the refrigerant inlet flow region of the flow passage 23A, in other words, a center 23 m from the opening orifice 23j and the final portion 23h from the third straight part 23g is defined as a straight line L3, and a distance between the center 23 m of the opening hole 23j and the final portion 23i of the third straight line 23g is defined as a straight line L4. An equivalent hydraulic diameter of the flow passage of the third straight portion 23g from the center 23m of the opening orifice 23j to the final portion 23h of the third straight portion 23g is defined as an equivalent hydraulic diameter De3, and a ratio of the straight distance L3 to the diameter equivalent hydraulic De3 is defined as a straight L3 / De3 ratio. An equivalent hydraulic diameter of the flow passage of the third straight portion 23g from the center 23m of the opening orifice 23j to the final portion 23i of the third straight portion 23g is defined as an equivalent hydraulic diameter De4, and a ratio of the straight distance L4 and the diameter equivalent hydraulic De4 is defined as a straight L4 / De4 ratio.
[0094] Figure 14 is a graph showing a relationship between the rectilinear ratio of the third rectilinear part and the distribution ratio in the flow passage formed in the third plate-shaped member of the heat exchanger according to Mode 1. Note that Figure 14 shows a change in the distribution ratio R in the flow passage 23A when the L3 / De3 rectilinear ratio (= L4 / De4) is changed in a state in which the L3 / De3 rectilinear ratio is set equal to the L4 rectilinear ratio / De4.
[0095] As shown in figure 14, the distribution ratio R is changed so that the distribution ratio R is increased until the L3 / De3 rectilinear ratio and the L4 / De4 rectilinear ratio reach 1.0, and the R distribution reaches 0.5 when the L3 / De3 rectilinear ratio and the L4 / De4 rectilinear ratio are 1.0 or greater. When the L3 / De3 rectilinear ratio and the L4 / De4 rectilinear ratio are less than 1.0, the distribution ratio R does not become 0.5 due to a region of the connecting part 23k, which communicates with the final 23h portion of the third rectilinear part 23g, and a region of the connecting part 231, which communicates with the final portion 21i of the third rectilinear part 23g are folded in different directions in relation to the gravity direction. That is, when the L3 / De3 rectilinear ratio and the L4 / De4 rectilinear ratio are set to 1.0 or higher, the uniformity in the refrigerant distribution can be further increased.
[0096] As shown in figures 9 and 10, an angle formed between a center line of the connecting part 23k and a center line of the third straight part 23g is defined as an angle θ1, and an angle formed between a center line of the connecting part 23k. connection 231 and the center line of the third straight part 23g defined as an angle θ2.
[0097] Figure l5 is a graph showing a relationship between a bending angle of the connection part and a distribution ratio in the flow passage formed in the third plate-shaped member of the heat exchanger according to Mode l. Note that figure l5 shows a change in the distribution ratio R in the flow passage 23A when the angle θl (= angle θ2) is changed in a state in which the angle θl is set equal to an angle θ2.
[0098] As shown in figure l5, as the angle θl and angle θ2 approach 90 degrees, the distribution ratio R approaches 0.5. That is, when the angle θl and the angle θ2 are increased, the uniformity in refrigerant distribution can be further increased. In particular, as illustrated in figure 6, in flow passage 23A, when the lower end 23c of the first rectilinear part 23a is positioned closer to the final portion 23h of the third straight portion 23g, and the upper end 23f of the second straight portion 23d is positioned closer to the final portion 23j of tpr23g, the uniformity in distribution of the refrigerant is further enhanced. <How to use heat exchanger>
[0099] Now, an example of how to use the heat exchanger according to Mode 1 is described.
[00100] Note that, in the following, a case is described which in which the heat exchanger is used for an air conditioner, but the present invention is not limited to such a case and, for example, the heat exchanger according to Mode 1 can be used for another refrigeration cycle device including a refrigerant circuit. In addition, a case is described in which the air conditioner switches between a cooling operation and a heating operation, but the present invention is not limited to such a case, and the air conditioning device can perform only the cooling operation. or the heating operation.
[00101] Figure 16 is a view illustrating the configuration of the air conditioning unit to which the heat exchanger according to Mode 1 is applied. Note that, in figure 16, the refrigerant flow during the refrigeration operation is indicated by the solid arrow, while the refrigerant flow during the heating operation is indicated by the dotted arrow.
[00102] As shown in figure 16, an air conditioner 51 includes a compressor 52, a four-way valve 53, a heat exchanger 54 on the side of the heat source, an expansion device 55, a heat exchanger from the load side 56, a heat source side fan 57, a load side fan 58, and a controller 59. Compressor 52, four-way valve 53, heat exchanger side heat exchanger 54 , an expansion device 55 and a charge side heat exchanger 56 are connected by refrigerant tubes to form a refrigerant circuit.
[00103] Controller 59 is connected, for example, to compressor 52, four-way valve 53, expansion device 55, heat source side fan 57, load side fan 58, and various sensors . Controller 59 switches the flow path of the four-way valve 53 to switch between the cooling operation and the heating operation. The heat exchanger on the heat source side 54 acts as a condenser during the cooling operation, and acts as an evaporator during the heating operation. The charge side heat exchanger 56 acts as the evaporator during the cooling operation, and acts as the condenser during the heating operation.
[00104] The flow of the refrigerant during the refrigeration operation is described.
[00105] The refrigerant in a state of high pressure and high temperature gas discharged from the compressor 52 passes through the four-way valve 53 to flow to the heat exchanger on the side of the heat source 54, and is condensed through the exchange of heat with the external air supplied by the fan on the heat source side 57 to thereby turn the refrigerant into a high pressure liquid state, which flows from the heat source side heat exchanger 54. The liquid refrigerant high pressure draining from the heat exchanger side of the heat source 54 flows to the expansion device 55 to become the refrigerant in a two-phase low pressure liquid-gas state flowing from the expansion device 55 draining to the heat exchanger heat from the charge side 56 to be evaporated through the exchange and heat with internal air supplied by the charge side fan 58 to thereby turn the refrigerant into a low pressure gas state, which drains from the heat exchanger. load side value 556. The refrigerant in the low pressure gas state flowing from the charge side heat exchanger 56 passes through the four-way valve 53 to be sucked into the compressor 52.
[00106] The flow of the refrigerant during the heating operation is described.
[00107] The refrigerant in a state of high pressure and high temperature gas discharged from the compressor 52 passes through the four-way valve 53 to flow to the heat exchanger on the charge side 56, and is condensed through the heat exchange as internal air supplied by the charge side fan 58 to thereby make the refrigerant into a high pressure liquid state, which flows from the charge side heat exchanger 56. The high pressure liquid refrigerant flowing from the heat exchanger Heat from the charge side 56 flows into the expansion device 55 to make the refrigerant in a low-pressure, two-phase gas-liquid state. The refrigerant in the low-pressure, two-phase gas-liquid state flowing from the expansion device 55 flows to the heat exchanger on the heat source side 54 to be evaporated by exchanging heat with the external air supplied by the fan on the side of the heat source. heat source 57 to thereby make the refrigerant into a low pressure gas state, which flows from the heat exchanger on the side of the heat source 54. the refrigerant in the low pressure gas state flowing from the heat exchanger of the heat source side 54 passes through the four-way valve 53 to be sucked into the compressor 52.
[00108] Heat exchanger 1 is used for at least one of the heat exchanger on the heat source side 54 or the heat exchanger on the load side 56. When heat exchanger 1 acts as an evaporator, the heat exchanger heat 1 is connected so that the refrigerant flows into it from the stack type collector 2, and the refrigerant drains from the collector 3. In other words, when the heat exchanger 1 acts as the evaporator, the refrigerant in the two-phase state liquid gas passes through the refrigerant tube of the first heat transfer tube 4 to flow into the stack type collector 2, and the refrigerant in the gaseous state passes through the first heat transfer tube 4 to flow into the collector 3 In addition, when the heat exchanger 1 acts as the condenser, the refrigerant in the gaseous state passes through the refrigerant pipe to flow into the collector 3, and the liquid refrigerant passes through the first heating pipe. heat transfer 4 to flow into the stack type collector 2. <Heat exchanger action>
[00109] Now, an action of the heat exchanger according to Mode 1 will be described.
[00110] The second plate-shaped unit 12 of the stack-type collector 2 has the distribution flow passage 12A formed therein, including branched flow passages 12b, each including the opening orifice 23j, the first rectilinear part 23a being parallel to the direction of gravity and having the lower end 23c in communication with pab23j through the connecting part 23k, and the second straight line 23d being parallel to the direction of gravity and having the upper end 23f in communication with the opening hole 23j through the of connection 23l. The refrigerant flowing into the branched flow passage 12b through the opening orifice 23j of the branched flow passage 12b passes through each of the connecting parts 23k and 23l, each having at least one part not parallel to the direction of gravity for cause deviation in a direction perpendicular to the direction of gravity and then the deviation is uniform in each of the first rectilinear part 23a and the second rectilinear part 23d. Then, the refrigerant flows from the branched flow passage 12b through one of the upper end 23b of the first straight portion 23a and the lower end 23e of the second straight portion 23d. Consequently, the leakage of the refrigerant from the branched flow passage 12b in the exiting cause of the bypass is suppressed, which increases the uniformity in distribution of the refrigerant.
[00111] Furthermore, the flow passage 23A formed in the third plate-shaped member 23 is a through-pass groove, and the branched flow passage 12b is formed by stacking the third plate-shaped member 23. Therefore, the processing and assembly are simplified, and production efficiency, manufacturing cost and the like are reduced.
[00112] In particular, when the heat exchanger 1 is used in an inclined manner, in other words, even when the arrangement direction of the first discharge flow passages 11A intersects the gravity direction, the branched flow passage 12b includes the first rectilinear part 23a and the second rectilinear part 23d, which are parallel to the direction of gravity and thus the leakage of the refrigerant from the branched flow passage 12b in the state of causing the deviation is suppressed, which increases uniformity in the distribution of soda.
[00113] In particular, in the stacking collector of the related technique, when the refrigerant flowing into it is in a two-phase state, the refrigerant is easily affected by gravity, making it difficult to equalize the flow and the quality of the refrigerant. draining into the heat transfer tube. In the stack 2 type manifold, however, despite the flow and quality of the refrigerant in the two-gas-liquid state flowing into it, the refrigerant is less likely to be affected by gravity, and the flow and quality of the refrigerant flowing to each heat transfer tube 4 can be equalized.
[00114] In particular, in the stacking collector of the related technique, when the heat transfer tube is changed from a circular tube to a flat tube with the purpose of reducing the amount of refrigerant or obtaining space savings in the heat exchanger, the stacking collector needs to be increased in size in every peripheral direction perpendicular to the direction of refrigerant inlet flow. On the other hand, stacking collector 2 is not required to be increased in every peripheral direction perpendicular to the direction of inlet flow, and thus space savings are achieved in heat exchanger 1. In other words, in the stacking collector of the technique correlated, when the heat transfer tube is changed from a circular tube to a flat tube, the cross-sectional area of the flow passage in the heat transfer tube is reduced and thus the pressure loss caused in the heat transfer tube heat is increased. Therefore, it is necessary to further reduce the angular interval between the plurality of grooves forming the branched flow passage to increase the number of paths (in other words, the number of heat transfer tubes), which causes an increase in the size of the stacking collector in the entire peripheral direction perpendicular to the direction of refrigerant inlet flow. On the other hand, in the stacker type 2 collector, even when the number of paths needs to be increased, the number of third plate-like members 23 only needs to be increased and, thus, the increase in size of the stacker type 2 collector in every direction peripheral perpendicular to the refrigerant flow direction is suppressed. Note that the stacking collector 2 is not limited to the case where the first heat transfer tube 4 is a flat tube. <Modified example 1>
[00115] Figure 17 is a perspective view of Modified Example 1 of the heat exchanger according to Mode 1 in a state in which the stacking collector is disassembled. Note that, in figure 17 and subsequent figures, a state in which the capping member on both sides 24 is stacked is illustrated (state in figure 7 and figure 8), but it goes without saying that a state in which the member of capping on both sides 24 is not stacked (state of figure 2 and figure 3) can be used.
[00116] As illustrated in figure 17, the second plate-shaped member 22 may have the plurality of flow passages 22A formed therein, in other words, the second plate-shaped unit 12 may have the plurality of first flow passages 22A. intake flow 12a formed therein, to thereby reduce the number of third plate-like members 23. With this configuration, the cost component, weight and the like can be reduced.
[00117] Figure 18 is a perspective view of Modified Example 1 of the heat exchanger according to Mode 1 in a state in which the stacking collector is disassembled.
[00118] The plurality of flow passages 22A may not be formed in regions opposite the refrigerant inlet flow regions of flow passages 23A formed in the third plate-shaped member 23. As illustrated in figure 18, for example, the a plurality of flow passages 22A can be formed collectively in one position, and a flow pass 25A of a different plate-shaped member 25 stacked between the second plate-shaped member 22 and the third plate-shaped member 23_1 can guide each of the refrigerant flows passing through the plurality of flow passages 22A to an opposite region {the refrigerant inlet flow region of flow passage 23A formed in the third plate-shaped member 23. <Modified example 2>
[00119] Figure 19 is a perspective view of Modified Example 2 of the heat exchanger according to Mode 1 in a state in which the stacking type collector is disassembled. As illustrated in Figure 19, any of the third plate-like members 23 can be replaced by a different plate-like member 25 having a flow passage 25B whose opening orifice 23j is not positioned in the third straight portion 23g. For example, in flow passage 25B, opening orifice 23j is not positioned in the third straight portion 23g, but positioned in an intersectional portion, and the refrigerant flows into the intersectional portion to be branched into four flows. The number and extensions can be any number. When the number of extensions is increased, the number of third plate-like members 23 is reduced. With such a configuration, uniformity in the distribution of the refrigerant is reduced, but the cost component, the weight and the like are reduced. <Modified example 3>
[00120] Figure 20 is a perspective view of the modified Example 3 of the heat exchanger according to Mode 1, in a state in which the stacking collector is disassembled. Figure 21 is a developed view of the stacking collector of modified Example 3 of the heat exchanger according to Mode 1. Note that, in Figure 21, the illustration of the capping member on both sides 24 is omitted.
[00121] As illustrated in figures 20 and 21, any of the third plate-shaped members 23 (e.g., the third plate-shaped member 23_2) may include flow passage 23A acting as the branched flow passage 12b for cause the refrigerant to flow from it to the side on which the first plate-shaped unit 11 is present without returning the refrigerant, and a flow passage 23B functioning as a branched flow passage 12b to cause the refrigerant to flow of the same by returning the refrigerant to a side opposite the side on which the first plate-shaped unit 11 is present. The flow passage 23B has a configuration similar to that of the flow passage 23A. In other words, the flow passage 23B includes the first straight portion 23a and the second straight portion 23d, which are parallel to the direction of gravity, and in the flow passage 23B, the refrigerant passes through the opening orifice 23j and flows out of it. through each of the upper end 23b of the first straight portion 23a and the lower end 23e of the second straight portion 23d. With such a configuration, the number of third plate-like members 23 is reduced, and the cost component, weight and the like are reduced. In addition, the frequency of occurrence of welding failure is reduced.
[00122] The third plate-shaped member 23 (for example, the third plate-shaped member 23_1) stacked on the third plate-shaped member 23 having the flow passage 23B formed on the opposite side to the sides on which the first plate-shaped unit 11 is present may include a flow passage 23C for returning refrigerant flowing there through flow passage 23B to flow passage 23A of the third plate-shaped member 23 having flow passage 23B formed therein without branching the refrigerant, or it may include flow passage 23A to return the refrigerant while branching the refrigerant. When the flow passage 23C is a flow passage including a straight line 23n parallel to the direction of gravity on a side over which the refrigerant flows, as shown in Figure 21, the uniformity in the distribution of the refrigerant can be further enhanced. <Modified example 4>
[00123] Figure 22 is a perspective view of modified Example 4 of the heat exchanger according to Mode 1 in a state in which the stacking collector is disassembled.
[00124] As illustrated in figure 22, a convex portion 26 can be formed on any of the plate-like member and capping member on both sides 24, in other words, a surface of any of the members to be stacked. For example, position, shape, size, etc. of the convex portion 26 are specific for each member to be stacked. The convex portion 26 can be a component such as a spacer. The stacked member adjacent to it has a concave portion 27 formed therein, into which the convex portion 26 is inserted. The concave portion 27 may or may not be a through hole. With such a configuration, the error in the lamination order of the members to be stacked is suppressed, which reduces the error rate. The convex portion 26 and the concave portion 27 can be adjusted together. In such a case, a plurality of convex portions 26 and a plurality of concave portions 27 can be formed, so that the members to be stacked are positioned through adjustment.
[00125] In addition, the concave portion 27 may not be formed, and the convex portion 26 may be fitted to a part of the flow passage of the stacked member adjacent thereto. In this case, the height, size, etc. of the convex portion 26 can be set at levels that do not inhibit the flow of refrigerant. <Modified example 5>
[00126] Figure 23 is a perspective view of the main part of the modified Example 5 of the heat exchanger according to Modality 1 in a state in which the stack type collector is disassembled. Figure 24 is a sectional view of the main part of the modified Example 5 of the heat exchanger according to Mode 1 in a state in which the stacking collector is disassembled. Note that figure 24 is a sectional view of the first plate-shaped member 21 taken along line A-A in figure 23.
[00127] As illustrated in figures 23 and 24, any of the plurality of flow passages 21A formed in the first plate-shaped member 21 can be tapered through the hole having a circular section in the surface of the first plate-shaped member 21 on the side on which the second plate-shaped unit 12 is present, and having a shape conformed to that of the outer peripheral surface of the first heat transfer tube 4 on the surface of the first plate-shaped member 21 on the side on the which retaining member 5 is present. In particular, when the first heat transfer tube 4 is a flat tube, the through hole is shaped to expand gradually in a region of the surface on the side on which the second plate-shaped unit 12 is present to the surface on the side on which the retaining member 5 is present. With such a configuration, the loss of refrigerant pressure when the refrigerant passes through the first outlet flow passage 11A is reduced. <Modified example 6>
[00128] Figure 25 is a perspective view of the main part of the modified Example 6 of the heat exchanger according to Mode 1 in a state in which the stacking collector is disassembled. Fig. 26 is a sectional view of the main part of modified Example 6 of the heat exchanger according to Mode 1 in a state in which the stacking collector is disassembled. Note that figure 26 is a sectional view of the third plate-like member 23 taken along line B-B in figure 25.
[00129] As illustrated in figures 25 and 26, any of the flow passages 23A formed in the third plate-like member 23 can be a bottom groove. In this case, a circular through hole 23q is formed in each of a final portion 23o and a final portion 23p of a bottom surface of the flow passage groove 23A functioning as the refrigerant partition flow passage between the branched flow passages. 12b which increases production efficiency. Note that in Figures 25 and 26m a case is illustrated in which the refrigerant flow side of the flow passage 23A is the bottom surface, but the refrigerant inlet flow side of the flow passage 23A may be the bottom surface. . In this case, a through hole can be formed in a region corresponding to the opening hole 23j. <Modified example 7>
[00130] Figure 27 is a perspective view of the modified Example 7 of the heat exchanger according to Mode 1 in a state in which the stacking collector is disassembled.
[00131] As illustrated in figure 27, flow passage 22A functioning as the first intake flow passage 12a can be formed in a member to be stacked other than the second plate-shaped member 22, in other words, in other words words, a different plate-shaped member, the capping member on both sides 24 or other members. In this case, the flow passage 22A can be formed, for example, as a through hole passing through the different plate-like member from its lateral surface to the surface on the side where the second plate-like member 22 is present. In other words, the present invention encompasses a configuration in which the first inlet flow passage 12a is formed in the first unit in form fg rlcec 3 3. gc “rcuucigo fg flwzq fg fkuVtkdwk>« q ”fc rtgugpVg kpxgp>« q covers dispensing flow passages other than dispensing flow pass 12A in which the first inlet flow pass 12a is formed in the second plate-shaped unit 12. Mode 2
[00132] A heat exchanger according to Mode 2 is described.
[00133] Note that superimposed description or description similar to that of Modality 1 is appropriately simplified or omitted. <Heat exchanger configuration>
[00134] Now, the configuration of the heat exchanger according to Mode 2 will be described.
[00135] Figure 28 is a view illustrating the configuration of the heat exchanger according to Mode 2.
[00136] As illustrated in figure 28m the heat exchanger 1 includes the stack type collector 2, the plurality of first heat transfer tubes 4, the retaining member 5, and plurality of fins 6.
[00137] The stack-type manifold 2 includes the refrigerant inlet flow port 2A, the plurality of refrigerant outlet flow ports 2Bm, a plurality of refrigerant inlet flow ports 2C, and a refrigerant inlet flow port 2C. 2D refrigerant. The refrigerant tubes are connected to the refrigerant inlet flow port 2A of the stacker manifold 2 and to the 2D refrigerant outlet flow port of the stacker manifold 2. The first heat transfer tube 4 is a flat tube subject to staple folding. The plurality of first heat transfer tubes 4 are connected between the plurality of refrigerant outlet flow ports 2B of the stack type collector 2 and the plurality of refrigerant inlet flow ports 2C of the stack type collector 2. <Flow of Refrigerant in Heat Exchanger>
[00138] Now, the flow of refrigerant in the heat exchanger according to Mode 2 will be described.
[00139] The refrigerant flowing through the refrigerant pipe passes through the refrigerant inlet flow port 2A to flow into the stack-type manifold 2 to be distributed and then passes through the plurality of refrigerant outflow holes. 2B to flow towards the plurality of first heat transfer tubes 4. In the plurality of first heat transfer tubes, the refrigerant exchanges heat with the air supplied by a fan, for example. The refrigerant passing through the plurality of first heat transfer tubes 4 passes through the plurality of refrigerant inlet flow orifices 2C to flow into the stack type manifold 2 to be joined, and thus passes through the refrigerant outflow orifice. 2D to flow towards the refrigerant pipe. The refrigerant can flow inversely. <Refrigerant configuration in the heat exchanger >>
[00140] Now, the stacking collector configuration of the heat exchanger according to Mode 2 will be described.
[00141] Figure 29 is a perspective view of the heat exchanger according to Mode 2 in a state in which the stack type collector is disassembled. Figure 30 is a developed view of the stacker collector of the heat exchanger according to Mode 2. Note that, in figure 30, the illustration of the capping member on both sides 24 is omitted.
[00142] As illustrated in figures 29 and 30, the stack type collector 2 includes the first plate-shaped unit 11 and the second plate-shaped unit 12. The first plate-shaped unit 11 and the second plate-shaped unit 12 are stacked on top of each other.
[00143] The first plate-shaped unit 11 has the plurality of first discharge flow passages 11A and a plurality of second inlet flow passages 11B formed therein. The plurality of second inlet flow passages 11B corresponds to the plurality of refrigerant inlet flow ports 2C in figure 28.
[00144] The first plate-like member 21 has a plurality of flow passages 21B formed therein. The plurality of flow passages 21B are each a through hole having an internal peripheral surface shaped conforming to an external peripheral surface of the first heat transfer tube 4. When the first plate-shaped member 21 is stacked, the plurality of flow passages 21B functions as the plurality of second inlet flow passages 11B.
[00145] The second plate-shaped unit 12 has the distribution flow passage 12A and a junction flow passage 12B formed therein. The junction flow passage 12B includes a mixing flow passage 12c and a second discharge flow passage 12d. The second discharge flow passage 12d corresponds to the refrigerant outlet flow port 2D in figure 28.
[00146] The second plate-shaped member 22 has a flow passage 22B formed therein. The flow passage 22B is a circular through hole. When the second plate-shaped member 22 is stacked, the flow passage 22B functions as the second discharge flow passage 12d. Note that a plurality of flow passages 22B, in other words, a plurality of second discharge flow passages 12d, can be formed.
[00147] The plurality of third member in plate form 23_1 to 23_3 has, respectively, a plurality of flow passages 23D_1 to 23D_3 formed therein. Each of the plurality of flow passages 23D_1 through 23D_3 is a rectangular through hole passing through substantially the entire region in the height direction of the third plate-shaped member 23. When the plurality of third plate-shaped members 23_1 a 23_3 is stacked, each of the flow passages 23D_1 through 23D_3 functions as the mixing flow pass 12c. The plurality of flow passages 23D_1 to 23D_3 may not be rectangular in shape. In the following, in some cases, the plurality of flow passages 23D_1 through 23D_3 can be referred to collectively as flow pass 23D.
[00148] In particular, it is preferred to stack the capping member on both sides 24 having a laminated brazing material on both surfaces between the respective plate-like members to supply the brazing material. The flow passage 24B formed in the capping member on both sides 24_5 stacked between the retaining member 5 and the first plate-shaped member 21 is a through hole having a shaped inner peripheral surface conforming to the outer peripheral surface of the first tube heat transfer 4. The flow passage 24B formed in the capping member on both sides 24_4 stacked between the first plate-shaped member 21 and the third plate-shaped member 23_3 is a circular through hole. The flow passage 24B formed in other capping members on both sides 24 stacked between the third plate-shaped member 23 and the second plate-shaped member 22 is a rectangular through hole passing substantially through the entire region in the height direction of the capping member on both sides 24. When the capping member on both sides 24 is stacked, the flow passage 24B functions as the refrigerant partition flow passage for the second intake flow passage 11B and the junction flow passage 12B.
[00149] Note that flow passage 22B functioning as the second discharge flow passage 12d can be formed into a different plate-shaped member other than the second plate-shaped member 22 of the second plate-shaped unit 12, the capping member on both sides 24 or other members. In this case, a notch can be formed, which communicates between a part of the flow passage 23D or the flow passage 24B and, for example, a side surface of the different plate-shaped member or the capping member on both sides. 24. The mixing flow passage 12c can be returned so that the flow passage 22B functioning as the second discharge flow passage 12d is formed in the first plate-shaped member 21. In other words, the present invention encompasses a configuration in which the second discharge flow passage 12d is formed pc rtkogktc wpkfcfg go fotoc fg rncec 33. gc "rcuucigo fg flwzq fg jwp>« q "of the present invention encompasses the union of flow passages other than the flow passage of junction 12B at which the second discharge flow passage 12d is formed in the second plate-shaped unit 12. <Coolant flow in the laminated collector>
[00150] Now, the flow of refrigerant in the stacker-type collector of the heat exchanger according to Mode 2 will be described.
[00151] As illustrated in figure 29 and figure 30, the refrigerant flowing from the flow passage 21A of the first plate-shaped member 21 to pass through the first heat transfer tube 4 flows into the flow passage 21B of the first member in the form of a plate 21. The refrigerant flowing into the flow passage 21B of the first plate-shaped member 21 flows into the flow passage 23D formed in the third plate-shaped member 23 to be mixed. The mixed refrigerant passes through the flow passage 22B of the second plate-shaped member 22 to flow from it towards the refrigerant pipe. <How to use the heat exchanger>
[00152] Now, an example of how to use the heat exchanger according to Mode 2 will be described.
[00153] Figure 31 is a diagram illustrating a configuration of an air conditioning device to which the heat exchanger according to Mode 2 is applied.
[00154] As illustrated in figure 31, heat exchanger 1 is used for at least one of the heat exchanger on the heat source side 54 or the heat exchanger preferably, load side 56. When the heat exchanger 1 acts as the evaporator, the heat exchanger 1 is connected so that the refrigerant passes through the distribution flow passage 12A of the stack type collector 2 to flow into the first heat transfer tube 4, and the refrigerant passes through of the first heat transfer tube 4 to flow into the junction flow passage 12B of the stacking-type manifold 2. In other words, when the heat exchanger 1 acts as the evaporator, the refrigerant in a two-phase gas- liquid passes through the refrigerant pipe to flow into the distribution flow passage 12A of the stack-type manifold 2, and the refrigerant in a gas state passes through the first heat transfer pipe 4 to and to slide into the junction flow passage 12B of the stacking collector 2.
[00155] In addition, when the heat exchanger 1 acts as the condenser, the refrigerant in a gas state passes through the refrigerant pipe to flow into the junction flow passage 12B of the stacker-type collector 2, and the refrigerant in liquid state passes through the first heat transfer tube 4 to flow into the distribution flow passage 12A of the stack-type collector 2. <Heat exchanger action>
[00156] Now, the action of the heat exchanger according to Mode 2 will be described.
[00157] In the stack type collector 2, the first plate-shaped unit 11 has the plurality of second inlet flow passages 12B formed therein. Consequently, the collector 3 is unnecessary and thus the cost component and the like. heat exchanger 1 are reduced. In addition, the collector 3 is unnecessary and, consequently, it is possible to extend the first heat transfer tube 4 to increase the number of fins 6 and the like, in other words, increase the assembly volume of the heat exchanger unit of the heat exchanger. heat 1. Mode 3
[00158] A heat exchanger according to Mode 3 will be described.
[00159] Note that the description superimposed or similar to each one of Modality 1 and Modality 2 is appropriately simplified or omitted. <Heat exchanger configuration>
[00160] Now, the configuration of the heat exchanger according to Mode 3 will be described.
[00161] Figure 32 is a view illustrating the configuration of the heat exchanger according to Mode 3.
[00162] As illustrated in figure 32, the heat exchanger 1 includes the stack type collector 2, the plurality of first heat transfer tubes 4, a plurality of second heat exchanger tubes 7, the retaining member 5 and the plurality of fins 6.
[00163] The stacking collector 2 includes a plurality of refrigerant return orifices 2E. Similar to the first heat transfer tube 4, the second heat exchanger tube 7 is a flat tube subject to clamp bending. The plurality of first heat transfer tubes 4 is connected between the plurality of refrigerant outlet flow holes 2B and the plurality of second heat exchanger tubes 7 is connected between the plurality of refrigerant return orifices 2E and the plurality of refrigerant outflow holes 2C from the stacking collector 2. <Coolant flow in the heat exchanger>
[00164] Now, the flow of refrigerant in the heat exchanger according to Mode 3 will be described.
[00165] The refrigerant flowing through the refrigerant pipe passes through the refrigerant inlet flow port 2A to flow into the stack-type manifold 2 to be distributed and then passes through the plurality of refrigerant outflow holes. 2B to flow towards the plurality of first heat transfer tubes 4. In the plurality of first heat transfer tubes 4, the refrigerant exchanges heat with the air supplied by the fan, for example. The refrigerant passing through the plurality of first heat transfer tubes 4 flows into the plurality of refrigerant return holes 2E of the stack type collector 3 to be returned, and drains from it towards the plurality of second heat exchanger tubes 7 In the plurality of second heat exchanger tubes 7, the refrigerant exchanges heat as air supplied by a fan, for example. The refrigerant flows passing through the plurality of second heat exchanger tubes 7 pass through the plurality of refrigerant inlet flow holes 2C to flow into the stack-type manifold 2 to be joined, and the joined refrigerant passes through the opening orifice. 2D refrigerant outlet flow to drain from it towards the refrigerant pipe. The refrigerant can flow inversely. <Laminated collector configuration>
[00166] Now, the stacking collector configuration of the heat exchanger according to Mode 3 will be described.
[00167] Figure 33 is a perspective view of the heat exchanger according to Mode 3 in a state in which the stack type collector is disassembled. Figure 34 is a developed view of the stacker collector of the heat exchanger according to Mode 3. Note that, in figure 34, the illustration of the capping member on both sides 24 is omitted.
[00168] As illustrated in figures 33 and 34, the stack type collector 2 includes the first plate-shaped unit 11 and the second plate-shaped unit 12. The first plate-shaped unit 11 and the second plate-shaped unit plate 12 are stacked on top of each other.
The first plate-shaped unit 11 has the plurality of discharge flow passages 11A, the plurality of second inlet flow passages 11B, and a plurality of return flow passages 11C formed therein. The plurality of return flow passages 11C corresponds {the plurality of refrigerant return orifices 2E in figure 32.
[00170] The first plate-like member 21 has a plurality of flow passages 21C formed therein. Each of the plurality of flow passages 21C is a through hole having an inner peripheral surface shaped to surround the outer peripheral surface of the final portion of the first heat transfer tube 4 on the refrigerant outlet flow side, and the peripheral surface of the final portion of the second heat exchanger tube 7 on the refrigerant inlet flow side. When the first plate-like member 21 is stacked, the plurality of flow passages 21C functions like the plurality of return flow passages 11C.
[00171] In particular, it is preferred to stack the capping member on both sides 24 having a strong solder material laminated on both surfaces between the respective plate-shaped members to supply the hard soldering material. The flow passage 24C formed on the capping member on both sides 24_5 stacked between the retaining member 5 and the first plate-shaped member 21 is a through hole having an inner peripheral surface shaped to surround the outer peripheral surface of the final portion of the first heat transfer tube 4 on the refrigerant outflow side and the outer peripheral surface of the final portion of the second heat exchanger tube 7 on the refrigerant inlet flow side. When the capping member on both sides 24 is stacked, the flow passage 24C functions as the refrigerant partition flow passage to the return flow passage 11C. <Coolant flow in the laminated collector>
[00172] Now, the flow of the refrigerant in the stacker collector of the heat exchanger according to Mode 3 will be described.
[00173] As illustrated in figure 33 and figure 34, the refrigerant flowing from the flow passage 21A of the first plate-shaped member 21 to pass through the first heat transfer tube 4 flows into the flow passage 21C of the first member in the form of a plate 21 to be returned and flow to the second heat exchanger tube 7. The refrigerant passing through the second heat exchanger tube 7 flows into the flow passage 21B of the first plate-shaped member 21. The refrigerant flowing into the flow passage 21B of the first plate-like member 21 flows into the flow passage 23D formed in the third plate-like member 23 to be mixed. The mixed refrigerant passes through the flow passage 22B of the second plate-shaped member 22 to flow from it towards the refrigerant pipe. <How to use the heat exchanger>
[00174] Now, an example of how to use the heat exchanger according to Mode 3 will be described.
[00175] Figure 35 is a diagram illustrating a configuration of an air conditioning device to which the heat exchanger according to Mode 3 is applied.
[00176] As illustrated in figure 35, heat exchanger 1 is used for at least one of the heat exchanger on the heat source side 54 or the heat exchanger on the load side 56. When heat exchanger 1 acts like the evaporator, the heat exchanger 1 is connected so that the refrigerant passes through the distribution flow passage 12A of the stack-type collector 2 to flow into the first heat transfer tube 4, and the refrigerant passes through the second heat exchanger tube 7 to flow into the stack flow manifold junction flow passage 12B 2. In other words, when heat exchanger 1 acts as the evaporator, the refrigerant in a two-phase gas-liquid state passes through of the refrigerant pipe to flow into the distribution flow passage 12A of the stack type collector 2, and the refrigerant in a gaseous state passes through the second heat exchanger pipe 7 to flow into the passage of f junction luxury 12B of the stacking manifold 2. In addition, when the heat exchanger 1 acts as the condenser, the refrigerant in a gaseous state passes through the refrigerant pipe to flow into the junction flow passage 12B of the stacking manifold 2, and the liquid refrigerant passes through the first heat transfer tube 4 to flow into the distribution flow passage 12A of the stack type collector 2.
[00177] In addition, when the heat exchanger 1 acts as the condenser, the heat exchanger 1 is arranged so that the first heat transfer tube 4 is positioned on the upstream side (windward side) of the flow current. air through the fan on the heat source side 57 or the charge side fan 58 in relation to the second heat exchanger tube 7. In other words, a relationship is obtained that between the flow of refrigerant from the second heat exchanger tube 7 and the first heat transfer tube 4 and the air flow are opposite each other. The refrigerant in the first heat transfer tube 4 has a lower temperature than the refrigerant in the second heat exchanger tube 7. The air current generated by the fan on the heat source side 57 or the fan on the charge side 58 has a lower temperature on the upstream side of the heat exchanger 1 than on the downstream side of the heat exchanger 1. As a result, in particular, the refrigerant can be sub-cooled (so-called sub-cooled) by the low temperature air stream draining on the upstream side of the heat exchanger 1, which increases the performance of the condenser. Note that the fan on the heat source side 57 and the load side fan 58 can be arranged on the windward or leeward side. <Heat exchanger action>
[00178] Now, the action of the heat exchanger according to Mode 3 will be described.
[00179] In the heat exchanger 1, the first plate-shaped unit 11 has the plurality of return flow passage 11C formed therein, and, in addition to the plurality of the first heat transfer tubes 4, the plurality of second exchange tubes heat 7 is connected. For example, it is possible to increase the area in a state of the front view of the heat exchanger 1 to increase the amount of heat exchange, but in this case, the housing that incorporates the heat exchanger 1 is increased in size. In addition, it is possible to shorten the gap between fins 6 to increase the number of fins 6, thereby increasing the amount of heat exchange. In this case, however, from the point of view of drainage performance, icing performance, and anti-dust performance, it is difficult to shorten the gap between fins 6 to less than about 1 mm and thus increase the amount of heat exchange may be insufficient. On the other hand, when the number of rows of the heat transfer tubes is increased as in the heat exchanger 1, the heat exchange rate can be increased without changing the area in the state of the front view of the heat exchanger 1, the interval between fins 6, or other features of the type. When the number of rows of heat transfer tubes is two, the amount of heat exchange is increased by about 1.5 times or more. Furthermore, the area in the front view state of the heat exchanger 1, the gap between fins 6, or other features of the type, can be increased.
[00180] In addition, the collector (stacking collector 2) is arranged only on one side of the heat exchanger 1. For example, when the heat exchanger 1 is arranged in a folded state along a plurality of side surfaces of the housing incorporating the heat exchanger 1 in order to increase the assembly volume of the heat exchange unit, the final portion may be misaligned in each row of the heat transfer tubes, due to the radius of curvature of the bent parts differ, depending on each row of heat transfer tubes. When the stacking collector 2, the collector (stacking collector 2) is arranged only on one side of the heat exchanger 1, even when the final portion is misaligned in each row of the heat transfer tubes, only the final portions on a side will need to be aligned, which increases the degree of freedom in the design, production efficiency and other issues compared to the case where the collectors (stacking type e2 collector and collector 3) are arranged on both sides of the heat exchanger 1 as in the heat exchanger according to Mode 1. In particular, the heat exchanger 1 can be folded after the respective members of the heat exchanger 1 are joined together, which further increases the production efficiency.
[00181] In addition, when the heat exchanger 1 acts as the condenser, the first heat transfer tube 4 is positioned on the windward side in relation to the second heat exchanger tube 7. When the collectors (stacking type collector 2 and collector 3) are arranged on both sides of the heat exchanger 1, as in the heat exchanger according to Mode 1, it is difficult to provide a temperature difference in the refrigerant for each row of heat transfer tubes to increase performance of the condenser. In particular, when the first heat transfer tube 4 and the second heat exchanger tube 7 are flat tubes, unlike a circular tube, the degree of freedom in folding is small and thus it is difficult to imagine providing the temperature difference in the refrigerant for each row of the heat transfer tubes by the deformation of the refrigerant flow passage. On the other hand, when the first heat transfer tube 4 and the second heat exchanger tube 7 are connected to the stack type collector 2, as heat exchanger 1, the temperature difference in the refrigerant is inevitably generated for each row of the heat transfer tubes. heat transfer, and obtaining the relationship that the refrigerant flow and the air flow are opposite to each other, can be easily accomplished without distorting the refrigerant flow passage.
[00182] The present invention has been described above with reference to Modalities 1 to 3, but the present invention is not limited to such modalities. For example, a part or all of the respective modalities, the respective modified examples, and the like can be combined. List of Reference Signs
[00183] 1 Heat exchanger, 2 stacking collector, 2A refrigerant inlet flow port, 2B refrigerant outflow port, 2C refrigerant inlet flow port, 3 collector, 3A inlet flow port refrigerant, 3B refrigerant outlet flow port, 4 first heat transfer tube, 5 retaining member, 6 fin, 7 second heat exchanger tube, 11 first plate-shaped unit, 11A first outlet flow passage, 11B second inlet flow passage, 11C return flow passage, 12 second plate-shaped unit, 12A distribution flow passage, 12B junction flow passage, 12a first intake flow passage, 12b branched flow passage , 12c mixed flow passage, 12d second discharge flow passage, 21 first plate-shaped member, 21A-21C flow passage, 22 second plate-shaped member, 22A, 22B flow passage, 23, 23_1 - 23_3 third member plate-shaped, 23A-23D, 23A_1 -23_3, 23D_1 - 23D_3 flow passage, 23a first straight part, 23b upper end of first straight part, 23c lower end of second straight part, 23d second straight part, 23e lower end of second straight portion, 23f upper end of second straight portion, 23g third straight portion, 23h, 23i final portion of second straight portion, 23j opening hole, 23k, 23l connecting portion, 23m center of opening hole, 23n straight portion, 23o, 23p bottom slot portion, 23q through hole, 24, 24_1- 24_5 capping member on both sides, 24A- 24C flow passage, 25 plate-shaped member, 25A, 25B flow passage, 26 convex portion , 27 concave portion, 51 air conditioner, 52 compressor, 53 four-way valve, 54 heat source side heat exchanger, 55 expansion device, 56 load side heat exchanger, 57 fan side c source alor, 58 load side fan, 59 controller.

权利要求:
Claims (15)
[0001]
1. Stacking collector (2), comprising: a first plate-shaped unit (11) having a plurality of first discharge flow passages (11A) formed therein; and a second plate-shaped unit (12) being mounted on the first plate-shaped unit (11) and having a first inlet flow passage (12a) formed therein and a distribution flow passage (12A) formed therein, the distribution flow passage (12A) being configured for refrigerant distribution, which passes through the first intake flow passage (12a) to flow into the second plate-shaped unit (12), for the plurality first discharge flow passages (11A) to flow the refrigerant from the second plate-shaped unit (12), characterized by the fact that the distribution flow passage (12A) comprises a branched flow passage (12b) comprising: an opening orifice (23j); a first rectilinear part (23a) parallel to a direction of gravity, the first rectilinear part (23a) having a lower end communicating with the opening orifice (23j) through a first connection part; and a second rectilinear part (23d) parallel to the direction of gravity, the second rectilinear part (23d) having an upper end communicating with the opening orifice (23j) through a second connection part, in which at least a part of the the first connection part and at least a part of the second connection part are not parallel to the direction of gravity, and in which the branched flow passage (12b) is configured to allow the refrigerant to flow into it through the opening orifice (23j), pass through each of the first connecting part and second connecting part to flow into each of the lower end of the first straight part (23a) and the upper end of the second straight part (23d), and drain of the branched flow passage (12b) through each of the upper end of the first straight part (23a) and a lower end of the second straight part (23d).
[0002]
2. Stacking collector (2) according to claim 1, characterized in that each of the first rectilinear part (23a) and the second rectilinear part (23d) has a flow passage length from the upper end to the lower end, which is three times or wider than the equivalent hydraulic diameter of the flow passage.
[0003]
3. Stacking type collector (2) according to claim 1 or 2, characterized by the fact that the branched flow passage (12b) further comprises a third rectilinear part (23g) perpendicular to the gravity direction, and in which the opening (23j) comprises a part between both ends of the third rectilinear part (23g).
[0004]
4. Stacking collector (2) according to claim 3, characterized by the fact that the third straight part (23g) has a flow passage length from a center of the opening orifice (23j) to each of both. ends of the third straight part (23g), which is once or wider than an equivalent hydraulic diameter of the flow passage.
[0005]
Stacking collector (2) according to any one of claims 1 to 4, characterized by the fact that the second plate-shaped unit (12) comprises at least one plate-shaped member having a flow passage formed in the same , and the fact that the branched flow passage (12b) is formed by closing a region of the flow passage formed in at least one plate-shaped member other than a refrigerant inlet flow region and a flow region of refrigerant outlet, by a member mounted adjacent to at least one member in the form of a plate.
[0006]
Stacking collector (2) according to any one of claims 1 to 5, characterized in that an arrangement direction of the upper end of the first straight part (23a) and the lower end of the second straight part (23d) is directed along an arrangement direction of the plurality of first discharge flow passages (11A).
[0007]
Stacking collector (2) according to any one of claims 1 to 6, characterized in that the first inlet flow passage (12a) comprises a plurality of first inlet flow passages (12a).
[0008]
Stacking collector (2) according to any one of claims 1 to 7, characterized in that the branched flow passage (12b) comprises a branched flow passage (12b) configured to cause the refrigerant to drain from the branched flow passage (12b) to a side on which the first plate-shaped unit (11) is present, and a branched flow passage (12b) configured to cause the refrigerant to flow from the branched flow passage (12b ) to a side opposite the side on which the first plate-shaped unit (11) is present.
[0009]
9. Stacking collector (2) according to claim 5, characterized by the fact that at least one plate-shaped member has a convex portion, which is specific to at least one plate-shaped member, and in which the convex portion is fitted in a flow passage formed in the mounted member adjacent to at least one plate-shaped member.
[0010]
10. Heat exchanger (1), characterized by the fact that it comprises: the stacking type collector (2) as defined in any one of claims 1 to 9; and a plurality of first heat transfer tubes (4) connected to the plurality of first discharge flow passages (11A), respectively.
[0011]
11. Heat exchanger (1) according to claim 10, characterized by the fact that the first plate-shaped unit (11) has a plurality of second inlet flow passages (11B) formed therein, for which the refrigerant passing through the plurality of first heat transfer tubes (4) flows, and in which the second plate-shaped unit (12) has a junction flow passage (12B) formed therein, the junction flow passage (12B) being configured to join the refrigerant flows together, which pass through the plurality of second inlet flow passages (11B) to flow into the second plate-shaped unit (12), to cause the refrigerant flows into a second discharge flow passage (12d).
[0012]
Heat exchanger (1) according to claim 10 or 11, characterized by the fact that each of the tubes of the plurality of first heat transfer tubes (4) comprises a flat tube.
[0013]
13. Heat exchanger (1) according to claim 12, characterized by the fact that each of the plurality of first discharge flow passages (11A) has an inner peripheral surface gradually expanding towards an outer peripheral surface of each one of the plurality of first heat transfer tubes (4).
[0014]
14. Air conditioning apparatus (51) comprising the heat exchanger (1) as defined in any of claims 10 to 13, characterized in that the distribution flow passage (12A) is configured to cause the refrigerant flow from the distribution flow passage (12A) towards the plurality of first discharge flow passages (11A) when the heat exchanger (1) acts as an evaporator.
[0015]
Air conditioning device (51) according to claim 14, characterized by the fact that the first plate-shaped unit (11) of the stacking-type collector (2) has a plurality of second inlet flow passages ( 11B) formed therein, into which the refrigerant passing through the plurality of first heat transfer tubes (4) flows, in which the second plate-shaped unit (12) of the stacking collector (2) has a passage junction flow (12B) formed therein, the junction flow passage (12B) being configured to join refrigerant flows together, which pass through the plurality of second inlet flow passages (11B) to flow into the second plate-shaped unit (12) to cause the refrigerant to flow into a second discharge flow passage (12d), wherein the heat exchanger (1) further comprises a plurality of seconds heat exchanger tubes (7) co connected to the plurality of second inlet flow passages (11B), respectively, and in which the plurality of first heat transfer tubes (4) is positioned on a windward side in relation to the plurality of second heat exchange tubes (7 ) when the heat exchanger (1) acts as a condenser.

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EP2998683B1|2021-06-23|

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JP5847913B1|2014-11-06|2016-01-27|住友精密工業株式会社|Heat exchanger|

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WO2017042866A1|2015-09-07|2017-03-16|三菱電機株式会社|Distributor, laminated header, heat exchanger, and air conditioner|

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KR101646761B1|2016-02-03|2016-08-08|임종수|Heat Exchanging Apparatus|

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CN107687726B|2016-08-03|2020-10-27|杭州三花研究院有限公司|Heat exchange device|

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EP3534091B1|2016-10-26|2021-10-06|Mitsubishi Electric Corporation|Distributor and heat exchanger|

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WO2018189892A1|2017-04-14|2018-10-18|三菱電機株式会社|Distributor, heat exchanger, and refrigeration cycle device|

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WO2019073610A1|2017-10-13|2019-04-18|三菱電機株式会社|Laminated header, heat exchanger and refrigeration cycle device|

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WO2019193713A1|2018-04-05|2019-10-10|三菱電機株式会社|Distributor and heat exchanger|

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EP3587990B1|2018-06-22|2021-01-27|Valeo Vyminiky Tepla, s.r.o.|Header box for heat exchanger with thermal decoupling|

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WO2020090015A1|2018-10-30|2020-05-07|三菱電機株式会社|Refrigerant distributor, heat exchanger, and air conditioning device|

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CN112923608B|2021-01-16|2021-12-28|西安交通大学|Refrigerant flow straightener for shell and tube heat exchanger|

法律状态:
2018-11-13| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|

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2019-12-10| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|

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2020-09-08| B06A| Notification to applicant to reply to the report for non-patentability or inadequacy of the application [chapter 6.1 patent gazette]|

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2020-12-29| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|

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2021-02-09| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 13/05/2014, OBSERVADAS AS CONDICOES LEGAIS. |

优先权:

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申请号 | 申请日 | 专利标题

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JPPCT/JP2013/063607|2013-05-15|

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PCT/JP2013/063607|WO2014184915A1|2013-05-15|2013-05-15|Laminated header, heat exchanger, and air conditioner|

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PCT/JP2014/062653|WO2014185391A1|2013-05-15|2014-05-13|Laminated header, heat exchanger, and air conditioner|

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