RU2643566C2 - Heat exchanger - Google Patents

Abstract

FIELD: heating system.

SUBSTANCE: in this document a heat exchanger is disclosed including a plurality of tubes arranged horizontally, a pair of vertical collectors, and at least one flow-distributing guide baffle fixed in one collector at the inlet of one group of collector groups such that a flow-distributing baffle is installed between the pipes of one group, wherein each of the at least one flow-distributing baffle is provided with at least one distribution opening providing passage of refrigerant therethrough.

EFFECT: heat exchanger prevents unbalanced distribution of refrigerant when it functions as an evaporator of an outdoor unit.

8 cl, 16 dwg

Description

FIELD OF TECHNOLOGY

[1] Embodiments of the present invention relate to a heat exchanger equipped with a vertical manifold having improved performance in distributing a refrigerant.

BACKGROUND

[2] A heat exchanger, which is a device that provides heat exchange of a refrigerant with outside air, generally includes pipes with a refrigerant passing through them, configured to heat exchange with outside air, heat exchange fins in contact with the pipes to increase the heat transfer area and a collector for communicating the ends of the pipes with each other to direct the refrigerant into the pipes and configured to carry the pipes.

[3] Heat exchangers include a finned type heat exchanger, which is performed by inserting a heat transfer pipe made of copper into a thin heat exchanger fin made of aluminum, and a heat exchanger of the parallel flow type, which is performed by installing a heat exchange fin between pipes having multiple microchannels and made of aluminum, and positioning the pipes so that they are carried by a pair of collectors. A parallel-flow heat exchanger is a type of relatively inexpensive and highly efficient device.

SUMMARY OF THE INVENTION

TECHNICAL PROBLEM

[4] In the embodiment where the heat exchanger of the parallel flow type and with vertical collectors is used as an evaporator of an outdoor unit, the distribution of the refrigerant from the vertical collectors through the pipes becomes unbalanced due to earth gravity and changes in the physical properties of the refrigerant depending from the physical phase of the refrigerant. In this case, the refrigerant can be distributed only in some pipes. For this reason, a heat exchanger of the parallel flow type is often used only as a condensing apparatus.

SOLUTION

[5] According to one aspect of the present invention, the heat exchanger includes a plurality of pipes arranged horizontally, a heat exchange rib in contact with the pipes, a first manifold arranged vertically to communicate with one end of each of the pipes, a second manifold arranged vertically to communicate with the other at the end of each pipe, at least one baffle forming a flow passage fixed to at least one collector from the first collector and the second collector and configured to extract the refrigerant flow passage by interrupting the refrigerant flow in at least one collector in the longitudinal direction and divide the pipes into n (n≥2, where n is an integer) groups, where each group has pipes adjacent to each other and providing the passage of the refrigerant in one direction through them, and the number of at least one forming the passage of the baffle flow is n-1, and at least one baffle distributing the flow, fixed in the corresponding collector from the first collector and a second manifold and located at the inlet of one group of n groups so that the flow distributing baffle is located between pipes belonging to one group, each of at least one flow distributing baffle provided with at least one distribution opening allowing refrigerant to pass through her.

[6] The flow distribution baffle can be fixed so that the flow distribution baffle is located between pipes belonging to the last group of n groups located in the flow direction of the refrigerant when the heat exchanger functions as an evaporator.

[7] The distribution hole may be spaced from the inner side surface of the corresponding manifold on the side opposite to the pipes of the corresponding manifold so that the flow of refrigerant along the inner side surface on the opposite side is interrupted.

[8] The cross section of each of the at least one distribution hole may have one of the following shapes: a polygon, a circle, and other different closed shapes.

[9] At least one distribution hole may include a hole made in the flow distribution partition and an opening made between the flow distribution partition and the inner side surface of the corresponding manifold while securing the flow distribution partition in the corresponding manifold.

[10] The total cross-sectional area of the at least one distribution hole may be from 1% to 40% of the cross-sectional area bounded by the inner surface of the respective manifold.

[11] Each of the groups can have from 2 to 15 pipes.

[12] Here n = 4, and the number forming at least one passage of the flow of partitions can be 3, and the pipes can be divided into four groups.

[13] One collector from the first collector and the second collector may be provided with an inlet pipe and an exhaust pipe, and the flow distributing baffle may be secured to another manifold from the first collector and the second collector.

[14] The refrigerant can pass up in the first collector and the second collector when the heat exchanger functions as an evaporator, and the refrigerant can pass down in the first collector and the second collector when the heat exchanger functions as a condensing apparatus.

[15] The heat exchanger may further include at least one flow-rate-increasing septum secured in a respective manifold of a first collector and a second collector located at the inlet of one group of n groups so that a flow-increasing septum is installed between one group and another a group mounted immediately ahead of one group in the direction of flow of the refrigerant when the heat exchanger functions as an evaporator, each of at least one enlarging the flow rate of the septum is provided with at least one accelerating hole, providing the passage of the refrigerant through it.

[16] At least one baffle increasing the flow rate may be installed between the last group of n groups located in the direction of flow of the refrigerant and another group located immediately in front of the last group when the heat exchanger functions as an evaporator.

[17] The cross section of each of the at least one accelerating hole may have one of the following shapes: a polygon, a circle, and another of different closed shapes.

[18] The total cross-sectional area of at least one accelerating hole may be from 5% to 70% of the cross-sectional area of the internal space of the corresponding collector.

[19] The total cross-sectional area of at least one accelerating hole may be larger than the total cross-sectional area of at least one distribution hole.

[20] According to another aspect of the present invention, the heat exchanger includes a plurality of pipes arranged horizontally, a heat exchange rib in contact with the pipes, a first manifold arranged vertically to communicate with one end of each of the pipes, a second manifold arranged vertically to communicate with the other at the end of each pipe, at least one baffle forming a flow passage fixed to at least one collector from the first collector and the second collector and configured to Create a refrigerant flow passage by interrupting the refrigerant flow in at least one collector in the longitudinal direction and divide the pipes into n (n≥2, where n is an integer) groups, where each group has pipes adjacent to each other and providing the passage of the refrigerant in one direction through them, and the number forming at least one passage of the flow of the baffles is n-1, and at least one increasing the flow rate of the baffle, fixed in the corresponding collector from the first collector and a second collector, located at the inlet of one group of n groups so that a flow-increasing partition is installed between one group and another group installed immediately in front of one group in the direction of refrigerant flow, when the heat exchanger functions as an evaporator, each of at least one increasing the flow rate of the partition is provided with at least one accelerating hole that allows the passage of the refrigerant through it.

[21] At least one baffle increasing the flow rate can be installed between the last group of n groups located in the direction of flow of the refrigerant and another group located immediately in front of the last group when the heat exchanger functions as an evaporator.

[22] The cross section of each of the at least one accelerating hole may take the form of one of the following: a polygon, a circle, and another of different closed shapes.

[23] The total cross-sectional area of at least one accelerating hole may be from 5% to 70% of the cross-sectional area of the internal space of the corresponding collector.

[24] According to another aspect of the present invention, the heat exchanger includes a plurality of pipes arranged horizontally, a heat exchange rib in contact with the pipes, a first manifold arranged vertically to communicate with one end of each of the pipes and provided with an inlet pipe and an outlet pipe, a second collector located vertically for communication with the other end of each of the pipes, at least one baffle forming a flow passage fixed to at least one collector from the first collector and the second of the collector and configured to form a refrigerant flow passage by interrupting the refrigerant flow in at least one collector in the longitudinal direction and divide the pipes into many groups, each of the groups having pipes adjacent to each other and allowing the refrigerant to pass through one direction through them, and at least one flow distributing baffle fixed in the second manifold so that the supply section of the second manifold for supplying refrigerant to the pipes belonging to one of the groups mounted on the uppermost side is divided into an upper section in communication with one pipe section and a lower section in communication with another pipe section, each of at least one flow distributing partition being provided with at least one distribution a hole that allows the refrigerant to pass through it, while one part of the refrigerant directed from the lower section to the upper section is distributed to one pipe section in communication with the upper section through at least a distribution hole, and another part of the refrigerant cannot pass through at least one distribution hole and is distributed to another pipe section in communication with the lower section.

[25] The heat exchanger may further include a baffle increasing the flow rate, secured in the second collector, to be installed between the supply section and the input section of the second collector and provided with at least one accelerating hole that allows the refrigerant to pass through it, and the input section is installed immediately under the feed section for receiving refrigerant from pipes of another one of the groups mounted immediately below the group mounted on the uppermost side, with the flow rate x odilnogo agent flowing from the input section of the feed section via at least one acceleration opening increases with pressure booster via the input section.

BEST MODES FOR CARRYING OUT THE INVENTION

[26] A parallel flow type heat exchanger with vertical manifolds according to an embodiment of the present invention can provide a balanced distribution of refrigerant flowing from the collectors to the pipes even when the heat exchanger functions as an evaporator of an outdoor unit. However, a decrease in heat transfer may not occur.

[27] Therefore, when a heat exchanger of the parallel flow type with vertical collectors is used in an outdoor unit of a heating and cooling system of the type of a heat pump, it can exhibit constant performance both in cooling and in heating.

BRIEF DESCRIPTION OF THE DRAWINGS

[28] The data and / or other aspects of the invention should be better understood and understood from the following description of embodiments with the accompanying drawings, in which the following is shown.

[29] In FIG. 1 shows the appearance of a heat exchanger according to an exemplary embodiment of the present invention.

[30] In FIG. 2 is a view of the disassembled second heat exchanger manifold shown in FIG. one.

[31] In FIG. 3 is a view of the disassembled first heat exchanger manifold shown in FIG. one.

[32] In FIG. 4 is a front view of the heat exchanger of FIG. one.

[33] In FIG. 5 shows the main parts of the heat exchanger of FIG. one.

[34] In FIG. 6 shows a section along line I-I of FIG. one.

[35] In FIG. 7 to 11 are cross-sectional views of flow distribution guide walls in accordance with other embodiments of the present invention.

[36] In FIG. 12 is a cross-sectional view of a flow rate-increasing guide wall of the heat exchanger of FIG. one.

[37] In FIG. 13 is a cross-sectional view of a manifold and a flow distribution guide wall according to another embodiment of the present invention.

[38] In FIG. 14 shows the entire refrigerant stream in a heating / cooling system according to an embodiment of the present invention.

[39] In FIG. 15 shows the flow of the refrigerant when the heat exchanger of FIG. 1 functions as a condensing apparatus.

[40] In FIG. 16 shows the flow of refrigerant when the heat exchanger of FIG. 1 functions as an evaporator.

MODE FOR THE INVENTION

[41] Embodiments of the present invention are described in detail below, examples of which are shown in the accompanying drawings, wherein reference numerals for like elements are the same throughout the description.

[42] In FIG. 1 shows an external view of a heat exchanger according to an exemplary embodiment of the present invention; FIG. 2 is a view of a disassembled part of the second collector of the heat exchanger of FIG. 1, and in FIG. 3 is a view of a disassembled part of the first collector of the heat exchanger of FIG. one.

[43] Shown in FIG. 1-3, the heat exchanger 10 is a heat exchanger of the parallel flow type and a vertical collector. The heat exchanger 10 includes a plurality of pipes 60 with a refrigerant passing through them arranged horizontally for heat exchange with outside air, a pair of collectors 20 and 30 arranged vertically to direct the refrigerant into the pipes 60 and communicating with the pipes 60, and a heat exchange fin 50 for pipe contact 60.

[44] Pipes 60 may be made of aluminum, have a flat shape and provided internally with microchannels 61 providing a through passage of the refrigerant. Pipes 60 are horizontal and spaced apart.

[45] The heat exchange fin 50 can take various forms, which increase the heat transfer area and facilitate the drainage of condensed water, and can be made of aluminum. The heat exchange fin 50 can be positioned between the pipes 60 and connected to the pipes 60 by soldering with a high temperature solder.

[46] The collectors 20 and 30 can be arranged vertically and spaced a predetermined distance from each other, with pipes 60 being placed between them. Below in this document, for simplicity of illustration, a manifold 20 located on the right side of the pipes 60, as shown in FIG. 1 is called the first collector 20, and the collector 30 located on the left side of the pipes 60 is called the second collector 30.

[47] The first collector 20 and the second collector 30 may be approximately cylindrical in shape with an interior space. Accordingly, the cross sections of the first collector 20 and the second collector 30 are approximately circular. However, embodiments of the present invention are not limited thereto. Cross sections may have an approximately “D” shape or other shapes.

[48] The first collector 20 and the second collector 30 can respectively be made by connecting the cylindrical bodies 21 and 31 with the inner spaces 22 and 32 and the opposite ends open to the upper covers 25 and 35 and the lower covers 26 and 36 covering the open opposite ends of the bodies 21 and 31. The housings 21 and 31, the upper covers 25 and 35, and the lower covers 26 and 36 can all be made of aluminum and soldered by high temperature solder.

[49] The holes 23 and 33 for the pipes, which enable the insertion of pipes 60 in them, are made on one side of each of the housings 21 and 31. The opposite ends of each of the pipes 60 can be inserted into the holes 23 and 33 for the pipes and connected to them by high-temperature soldering solder. In this case, the microchannels 61 of the pipes 60 can communicate with the inner space 22 and 32 of the first collector 20 and the second collector 30, and a refrigerant can pass between the collectors 20 and 30 and the pipes 60.

[50] The other sides of the housing 21 and 31 are provided with openings 24 and 34 for the guide walls to allow the insertion of the guide walls 70, 80, 90 and 100. The guide walls 70 forming the flow passage can be inserted into the holes 24 under the guide walls of the first collector 20 A guide baffle forming a flow passage 70, a flow baffle 100 increasing the flow rate, and flow baffles 80 and 90 distributing the flow can be inserted into openings 34 under the guide baffles of the second lecturer 30.

[51] The configurations and functions of the flow passage forming guide wall 70, increasing the flow rate of the guide wall 100 and flow distributing guide walls 80 and 90 are described in detail below. The guide walls 70, 80, 90 and 100 can be inserted into the holes 24 under the guide walls of the first collector 20 or the second collector 30 in the direction inward from the outer surface of the heat exchanger 10.

[52] The guide walls 70, 80, 90 and 100 can all be made of aluminum and connected to the holes 24 for the guide walls by soldering with high-temperature solder after being inserted into the holes 24 under the guide walls.

[53] In this case, the first manifold 20 may be provided with an inlet pipe 27 and an exhaust pipe 28, through which the refrigerant enters and leaves the first collector 20. The inlet pipe 27 may be equipped at the bottom of the first manifold 20, and the exhaust pipe 28 may be equipped at the top of the first manifold 20.

[54] When the heat exchanger 10 functions as an evaporator of an outdoor unit in this embodiment, the refrigerant in a liquid or gaseous state can be introduced through the inlet pipe 27. The introduced refrigerant can be converted into steam after absorbing heat from the outside air as it passes through pipes 60. Then the refrigerant can be discharged through the exhaust pipe 28 in a gaseous state.

[55] When the heat exchanger 10 functions as a condensing apparatus of an outdoor unit in this embodiment, the refrigerant in a gaseous state can be introduced through the exhaust pipe 28. The introduced refrigerant can transfer heat to the outside air as it passes through the pipes 60. Then, the refrigerant can condense into a liquid state and be discharged through inlet pipe 27.

[56] The heat exchanger 10, which can function as an evaporator and condensation apparatus of an outdoor unit with vertical collectors 20 and 30, as described above, is a parallel flow type heat exchanger. In particular, when the heat exchanger 10 functions as an evaporator of an outdoor unit, the flow-distributing guide walls 80 and 90 and the flow-increasing guide wall 100, equipped in the second manifold 30, can provide uniform distribution of the refrigerant, while improving heat transfer efficiency.

[57] The following is a detailed description of the configurations and functions of the flow-guiding partition wall 70, distributing the flow of the guiding walls 80 and 90, and increasing the flow rate of the guiding partition 100.

[58] In FIG. 4 is a front view of the heat exchanger of FIG. 1, in FIG. 5 shows the main parts of the heat exchanger of FIG. 1, and in FIG. 6 shows a section along line I-I of FIG. 1. In FIG. 7 to 11 are cross-sectional views of flow distributing guide walls in accordance with other embodiments of the present invention. In FIG. 12 is a cross-sectional view of a flow rate-increasing guide wall of the heat exchanger of FIG. 1. In FIG. 13 is a cross-sectional view of a manifold and a flow distributing guide wall according to another embodiment of the present invention.

[59] The arrows in FIG. 4 and 5, the refrigerant stream is indicated when the heat exchanger 10 functions as an evaporator of an outdoor unit.

[60] In FIG. 4-6, two flow barriers 70 formed on the first manifold 20 and one flow barr 70 on the second manifold 30 are formed. Thus, the heat exchanger 10 is provided with three flow barriers 70 which are mounted on different vertical marks.

[61] Three flow-forming guide walls 70 interrupt the flow of refrigerant in the manifolds 20 and 30 in the longitudinal direction of the manifolds 20 and 30. Accordingly, the refrigerant introduced into the first manifold 20 through an inlet pipe 27 equipped at the bottom of the first manifold 20, rises in a zigzag fashion, constantly passing through the first collector 20, pipes 60 and the second collector 30, as indicated by the arrows in FIG. four.

[62] Thus, the flow passage guiding partitions 70 form the flow passage of the refrigerant. At this stage, the pipes 60 are classified into many groups A, B, C and D. The pipes classified into one group are adjacent to each other and provide a through passage of the refrigerant in one direction.

[63] In this embodiment, the pipes 60 are divided into pipes of one group (group A below) located adjacent to each other at the lowest position and allowing the refrigerant to pass from the first manifold 20 to the second manifold 30 through them, the pipes of another groups (below in this document, group B) located adjacent to each other on pipes of group A and ensuring the passage of the refrigerant from the second manifold 30 to the first manifold 20 through them, pipes of another group (below in this document, group C), p located adjacent to each other on the pipes of group B and allowing the refrigerant to pass from the first manifold 20 to the second collector 30 through them, and pipes of another group (below in this document, group D) located adjacent to each other on the pipes of group C and providing the passage of the refrigerant from the second collector 30 to the first collector 20 through them. In this document, each of the groups may include 2-15 pipes.

[64] As described above, the heat exchanger 10 of this embodiment is provided with three guide baffles 70 forming the flow passage and the tubes 60 are divided into four groups by three flow passage forming baffles 70.

[65] In this document, the first collector 20 of a pair of collectors 20 and 30 is provided with both an inlet pipe 27 and an exhaust pipe 28. In this context, when the number of flow guides 70 forming the flow passage is n-1, where n is the number of pipe groups, where n is an integer greater than 2.

[66] Embodiments of the present invention are limited in terms of the number of flow guides 70 and the number of tube groups. Depending on the technical requirements, the number of guide baffles 70 forming the flow passage can be more or less than 3, and the number of pipe groups can also be more or less than the number shown in FIG. four.

[67] In short, a heat exchanger according to an embodiment of the present invention may have n-1 flow-guiding baffles that divide the pipes 60 into n (n≥2, where n is an integer) groups, each of which has pipes adjacent to each other and providing passage of the refrigerant in one direction.

[68] In this case, the flow distributing guide walls 80 and 90 are equipped to ensure uniform distribution of the refrigerant in the manifold 30 through the pipes 60. In this embodiment, two flow distributing guide walls 80 and 90 are installed in the upper part of the second manifold 30.

[69] The number of flow distributing guide walls is not limited. Depending on various factors, for example, the number and length of pipes 60 and the pressure of the refrigerant, it is possible to equip one flow distributing guide wall or three or more guide walls.

[70] The two flow-distributing guide walls 80 and 90 of this embodiment have substantially the same shape and function, and therefore, only the flow-distributing guide wall 80 located at the bottom of the two flow-distributing guide walls 80 and 90 is described below.

[71] The shape of the flow distributing guide wall 80 should be considered first. As shown in FIG. 6, the flow distributing guide wall 80 may include an interruption wall 89 located perpendicular to the longitudinal direction of the collector to interrupt the flow of refrigerant in the collector in the longitudinal direction of the collector, a distribution hole 81 formed in the interruption wall 89 to allow passage of the refrigerant in the collector in the longitudinal the direction of the collector, and the stopper 88 protruding from opposite sides of the interruption wall 89 to limit the depth of insertion guide rail current 80.

[72] The interruption wall 89 may be in contact with the inner side surface of the manifold to interrupt the flow of the refrigerant, and thus the refrigerant directed to the flow distributing guide wall 80 can be allowed to pass through the flow distributing guide wall 80 only through the distribution hole 81.

[73] In particular, the distribution hole 81 requires a reference distance G from the inner side surface 37 on the side opposite to the pipes facing the manifold, and the liquid refrigerant flow along the inner side surface 37 on the side opposite to the side to the pipes, interrupted.

[74] The distribution hole 81 may be of any shape. In addition, the number of distribution openings is not limited. The distribution hole shown in FIG. 6 has a rectangular section. However, embodiments of the present invention are not limited thereto. For example, the flow distributing guide baffle 82 may have a circular distribution bore 82a, as shown in FIG. 7. Alternatively, the flow distributing guide wall 83 may have a distribution hole 83a, in cross section of which several slots are formed, as shown in FIG. 8. Alternatively, the flow distribution guide wall 84 may have a distribution hole 84a with a cross-sectional shape different from a circle and a rectangle, as shown in FIG. 9. Alternatively, the flow distribution guide wall 85 may have a mesh distribution hole 85a, as shown in FIG. 10.

[75] The distribution hole of the flow distributing guide wall 82 includes not only the hole formed in the flow distributing guide wall 82, but also an opening formed between the flow distributing guide wall 82 and the manifold when securing the flow distributing guide wall 82 in the manifold.

[76] That is, an opening 86a formed between one surface 86b of the flow distributing guide wall 82 and the inner side surface 38 of the manifold 31 when securing the flow distributing guide wall 86 in the collector 31 is also created as the distribution hole 86a of the flow distributing guide wall 86, as shown in FIG. eleven.

[77] Moreover, the flow distributing guide wall 80 is applicable not only to a collector having a circular cross section, but also to a collector having a cross section with a shape different from a circle.

[78] That is, even in the embodiment where the cross section of the manifold 39 is approximately “D” -shaped, as shown in FIG. 13, a flow distributing guide baffle 87 with a distribution hole 87a may be secured to a manifold 39.

[79] The sum of the cross-sectional area of the distribution hole 81 in the flow-distributing guide wall 80 can be from 1 to 40% of the cross-sectional area of the inner space of the collector.

[80] The fixing position and function of the flow distributing guide wall 80 are described later herein with reference to FIG. 5.

[81] For ease of illustration, the portion of the interior of the second manifold 30 that supplies the refrigerant to the pipes of group D is defined as a supply section 40. At the same time, the lower end of the supply section 40 in the second manifold is limited by the guide wall 100 increasing the flow rate and its upper end is limited by the top cover 35.

[82] In the supply section 40, the refrigerant generally moves upward. In particular, the liquid refrigerant rises rapidly along the inner side surface of the second manifold 30 facing the pipes 60. Accordingly, the refrigerant is unevenly distributed along the pipes of group D in the supply section 40. That is, the refrigerant is for the most part distributed over some of the pipes of group D that are installed on the upper side, and a small portion of the refrigerant is distributed over the other pipes of group D installed on the lower side.

[83] The flow distributing guide wall 80 according to one embodiment is installed in the supply section 40 to ensure uniform distribution of the refrigerant of the supply section 40 across all pipes of group D.

[84] Specifically, the flow distributing guide wall 80 is secured in the second manifold 30 so as to be located between the pipes of group D. In this document, positioning the flow distributing guide wall 80 between the pipes of group D means that at least one of the pipes of group D is installed above a flow distributing guide wall 80, and at least one of a group D pipe is installed under the flow distributing guide wall 80.

[85] The feed section 40 is divided into two spaces by the flow distributing guide wall 80. For simplicity of illustration, one of the two spaces mounted above the flow distributing guide wall 80 is defined as the upper section 41, and the other space installed under the flow distributing guide wall 80, defined as lower section 42.

[86] The refrigerant flow is directed upward in the supply section 40, and thus the refrigerant passes from the lower section 42 to the upper section 41. At this stage, the refrigerant flowing from the lower section 42 to the upper section 41 is interrupted by the flow distributing guide wall 80 since the flow distributing guide wall 80 is installed between the lower section 42 and the upper section 41. In this case, only part of the refrigerant passes into the upper section 41 through the distribution hole 81, the other part of the refrigerant The entrant cannot pass through the distribution hole 81 and is forced to pass horizontally into pipes connected to the lower section 42.

[87] In particular, the liquid distributing agent rapidly rising along the inner side surface of the manifold facing the pipes is resisted by the flow distributing guide wall 80, mixing of the refrigerant may take place in the lower section 42.

[88] Through the above-described structural configuration, the flow distributing guide wall 80 can improve the distribution of the refrigerant in the pipes 60 in the manifold 30.

[89] Although the flow distributing guide wall 80 of this embodiment is shown to be mounted on top of a second manifold in communication with group D pipes, embodiments of the present invention are not limited to this. The flow distributing guide wall can be installed in any part of the second collector, where the fast flow causes uneven distribution of the refrigerant, according to the technical characteristics of the refrigerant of the heat exchanger.

[90] At the same time, a guide wall 100 increasing the flow rate is equipped to increase the flow rate of the refrigerant in the manifold 30 to improve the distribution of the refrigerant. In this embodiment, one flow-increasing guide bar 100 is fixed in the middle of the second manifold 30.

[91] The number of flow-increasing guide walls 100 is not limited thereto. Depending on the technical characteristics of the heat exchanger, two or more guiding partitions increasing the flow rate can be equipped. If not necessary, they can not be equipped.

[92] With respect to the configuration of the flow-rate-increasing guide wall 100, the flow-speed-increasing guide wall 100 has at least one acceleration opening 101 allowing the refrigerant to pass through it, as shown in FIG. 12. Increasing the flow rate of the guide wall 100 has a shape almost identical to the flow distributing guide wall 80.

[93] The sum of the cross-sectional area of at least one accelerating hole 101 in the flow-increasing guide wall 100 can be from 5% to 70% of the cross-sectional area of the inner space of the collector. Accordingly, the sum of the cross-sectional area of at least one accelerating hole 101 in the flow-increasing guide wall 100 is generally larger than the total cross-sectional area of at least one distribution hole 81 in the flow-distributing guide wall 80.

[94] The shape of the acceleration hole 101 in the flow-increasing guide wall 100 is not limited. Unlike the distribution hole 81 in the flow distributing guide wall 80, the acceleration hole 101 in the flow-increasing guide wall 100 is not necessarily spaced from the inner side surface of the manifold facing the pipes.

[95] Hereinafter, the fixing position and the function of increasing the flow rate of the guide wall 100 with reference to FIG. 5.

[96] For simplicity of illustration, the portion of the interior of the second manifold 30, mounted under the supply section 40 for receiving refrigerant from the pipes of group C, should be defined as the input section 43.

[97] The guide wall 100 increasing the flow rate is fixed in the second manifold 30 so that it is installed between the supply section 40 and the input section 43. That is, the guide wall 100 increasing the flow rate is fixed in the second manifold 30 so that it is located between the pipes of group D and the pipes of group C.

[98] In the inlet section 43, the refrigerant is allowed to pass upward to the section 40 by the refrigerant introduced from the pipes of group C. At this stage, the refrigerant passing from the inlet section 43 to the supply section 40 is interrupted because the flow-increasing guide wall 100 installed between the feed section 40 and the input section 43. The pressure of the refrigerant in the input section 43 increases.

[99] Accordingly, the flow rate of the refrigerant passing from the input section 43 to the supply section 40 increases when the refrigerant passes through the acceleration hole 101 in the flow-increasing guide wall 100.

[100] In this case, in the embodiment where the refrigerant passes in the manifold 30 at a low speed and, therefore, there is insufficient supply to the upper end of the collector 30 and concentration on the lower portion of the collector, the flow rate can be increased by installing a guide wall increasing the flow rate. In an embodiment where a sufficient volume of refrigerant is supplied to the upper end, a guide wall increasing the flow rate may not be required.

[101] In FIG. 14 shows the entire refrigerant stream in a heating / cooling system according to an embodiment of the present invention, FIG. 15 shows the flow of the refrigerant when the heat exchanger of FIG. 1 functions as a condensation apparatus, and in FIG. 16 shows the flow of refrigerant when the heat exchanger of FIG. 1 functions as an evaporator.

[102] The following describes the operation of a heating / cooling system with a heat exchanger according to an embodiment of the present invention with reference to FIG. 14-1.

[103] A double-acting heat pump, the heating and cooling system may include an outdoor unit 1 and an indoor unit 2. An outdoor unit 1 may include a first heat exchanger 10 according to one embodiment, a compressor 3 for refrigerant compression and an expansion unit 4 for expanding the refrigerant and a switching valve 5 for switching the flow path of the refrigerant, and the indoor unit 5 may include I am the second heat exchanger 5.

[104] In the cooling mode, the refrigerant passes sequentially through the compressor 3, the first heat exchanger 10, the expansion unit 4 and the second heat exchanger 5 along the solid arrows. Accordingly, the first heat exchanger 10 functions as a condensing apparatus and the second heat exchanger 5 functions as an evaporator.

[105] As shown in FIG. 15, in cooling mode, a gaseous refrigerant converted into a high temperature and high pressure refrigerant in the compressor 3 is introduced into the exhaust pipe 28 of the first heat exchanger 10. The introduced refrigerant condenses, transferring heat to the outside air as it passes down a zigzag path . The condensed refrigerant is discharged through the inlet pipe 27.

[106] In the heating mode, the refrigerant passes sequentially through the compressor 3, the second heat exchanger 5, the expansion unit 4 and the first heat exchanger 10 along the dotted arrows. Accordingly, the first heat exchanger 10 functions as an evaporator and the second heat exchanger 5 functions as a condensing apparatus.

[107] As shown in FIG. 16, in heating mode, a liquid or gaseous refrigerant converted to a low temperature and low pressure refrigerant during expansion in the expansion unit 4 is introduced into the inlet pipe 27 of the first heat exchanger 10. The introduced refrigerant is converted to steam by absorbing heat when it passes up the zigzag path. The vaporized refrigerant is discharged through the exhaust pipe 28.

[108] When the first parallel flow type heat exchanger 10 having vertical headers functions as an evaporator, the distribution of the refrigerant may become unbalanced due to the physical properties of the liquid refrigerant and earth gravity.

[109] In particular, the flow rate of the refrigerant rising upward in the second manifold 30 may be high, and thus, the refrigerant may tend to concentrate on the upper end of the second manifold 30. To prevent this unbalanced flow, at least one distributor the flow guide wall 80, 90 may be secured in a second manifold 30 of the first heat exchanger 10.

[110] In addition, the flow rate of the refrigerant rising upward in the second manifold 30 may be low, and thus the supply of the refrigerant may not be sufficient at the upper end of the second manifold 30. To prevent this unbalanced flow, at least one increasing The flow rate of the guide wall 100 can be fixed in the second manifold 30 of the first heat exchanger 10.

[111] Moreover, even when the first heat exchanger 10 functions as an evaporator of an outdoor unit, the refrigerant is distributed evenly. The problem of unbalanced operation of the heat pump heating and cooling system in cooling mode and heating mode can be resolved.

Claims (17)

1. A heat exchanger containing: many pipes arranged horizontally; heat exchange rib for contact with pipes; a first manifold arranged vertically for communication with one end of each of the pipes; a second manifold arranged vertically for communication with the other end of each of the pipes; at least one diaphragm forming a passageway installed in at least one collector of a first collector and a second collector and configured to form a passage of refrigerant flow by interrupting the flow of refrigerant in at least one collector in the longitudinal direction and separating the pipe into n (n≥2, where n is an integer) of groups, each of the groups having pipes adjacent to each other and allowing the refrigerant to pass in one direction through them, and the number of n forming septum at one flow passage is n-1; at least one flow distribution partition installed in at least one manifold of the first manifold and the second manifold so that the flow distribution partition is installed between pipes belonging to one group, each of at least one flow distribution partition being provided with at least one distribution opening allowing the refrigerant to pass through it, and at least one partition increasing the flow rate, installed in at least one collector from the first collector and the second collector immediately in front of one of n groups in which the refrigerant moves in one parallel direction, and immediately after the neighboring group in which the refrigerant moves in the opposite direction, each of at least one speed-increasing partition wall provided with at least one speed-increasing hole. 2. The heat exchanger according to claim 1, wherein the flow distributing baffle is installed so that the flow distributing baffle is installed between pipes belonging to the last group of n groups located in the direction of flow of the refrigerant when the heat exchanger functions as an evaporator. 3. The heat exchanger according to claim 1, in which the distribution hole is spaced from the inner side surface of the corresponding manifold on the side opposite to the pipes of the corresponding manifold so that the flow of the refrigerant along the inner side surface on the opposite side is interrupted. 4. The heat exchanger according to claim 1, in which the cross section of each of the at least one distribution hole has one of the following shapes: a polygon, a circle, and other different closed shapes. 5. The heat exchanger according to claim 1, in which at least one distribution hole is a hole made in the flow distribution partition. 6. The heat exchanger according to claim 1, in which: one collector from the first collector and the second collector is provided with an inlet pipe and an exhaust pipe; and a flow distributing partition is installed in another collector from the first collector and the second collector. 7. The heat exchanger according to claim 1, in which at least one flow-increasing partition is installed between the last group of n groups located in the direction of flow of the refrigerant and another group located immediately in front of the last group when the heat exchanger functions as an evaporator. 8. The heat exchanger according to claim 1, in which the cross section of each of at least one accelerating hole has one of the following shapes: a polygon, a circle, and other different closed shapes.

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