Plate-type heat exchanger

Abstract

The present invention relates to a plate-type heat exchanger and, more specifically, to a plate-type heat exchanger having a structure capable of increasing heat exchange performance by increasing internal pressure. The plate-type heat exchanger having the aforementioned structure of the present invention was conceived to solve the aforementioned problems, and the purpose of the present invention is to achieve the effect of satisfying high pressure resistance performance by minimizing the cross-sectional area of a flow path through which a refrigerant flows by means of alternating formation of the flow path in the upper and lower sections.

Description

plate heat exchanger

[0001] The present invention relates to a plate heat exchanger, and more specifically, to a plate heat exchanger having a structure capable of increasing heat exchange performance by increasing internal pressure.

[0002]

[0003] Heat exchangers are commonly used in indoor heating and cooling systems or battery cooling systems (e.g. chillers, water-cooled condensers). Generally, plate heat exchangers applied to vehicle heating and cooling systems are characterized by forming passages between plates of a certain thickness to allow fluid to flow, and arranging a number of plates at a certain interval to allow different fluids to flow through the passages one by one. Existing plate heat exchangers adopt a structure that forms embossing on the plates or inserts inner fins to improve the heat exchange performance of the working fluid.

[0004] Conventional plate heat exchangers have mainly used environmentally friendly refrigerant R744, but the existing method of simply forming an emboss on the plate or inserting an inner fin had limitations in changing the size, making it difficult to meet the pressure requirements of refrigerant R774.

[0005]

[0006] The present invention has been devised to solve the above problems, and the purpose of the present invention is to provide a plate heat exchanger that satisfies high pressure performance by forming the flow paths through which the refrigerant flows in an alternating manner from top to bottom, thereby minimizing the cross-sectional area of ​​the flow paths.

[0007] In addition, the present invention provides a plate heat exchanger that maximizes the shape and heat exchange area of ​​beads that control the flow of coolant, minimizes the dead volume of coolant, and maximizes the flow area of ​​coolant by forming the inlet and outlet of coolant and cooling water to be biased toward the corner ends.

[0008]

[0009] In order to solve the above-described problem, a plate heat exchanger according to one embodiment of the present invention includes a first heat exchange part and a second heat exchange part that are stacked in a predetermined stacking direction, and a flow path section through which a predetermined first fluid or second fluid flows, the heat exchange part for heat-exchanging the first fluid and the second fluid, and an end plate in the shape of a plate that is stacked in the stacking direction on one side of the first heat exchange part, wherein the first heat exchange part and the second heat exchange part include a plurality of plates that are stacked in the stacking direction, and the flow path section is characterized in that at least one of the plates is formed by bending to form a flow path for a working fluid.

[0010] In addition, the first heat exchange part is characterized in that it includes at least one first upper plate and a first lower plate whose one side is in contact with each other to form a predetermined space therebetween, the first upper plate includes a first bent portion formed on one side to protrude toward the opposite side of the first lower plate, and the first lower plate includes a second bent portion formed on one side to protrude toward the opposite side of the first upper plate.

[0011] In addition, the first bending portion and the second bending portion include two or more predetermined bending parts that are formed to extend in a predetermined direction, and both ends of each bending part included in the first bending portion correspond to both ends of each bending part included in the second bending portion and are connected to each other.

[0012] In addition, each bending part is characterized by being formed by extending in a diagonal direction that forms a predetermined angle rather than being vertical or horizontal to the direction of fluid flow.

[0013] In addition, the bending part included in the first bending part is formed to be inclined at a predetermined angle to one side from the direction of fluid flow, and the bending part included in the second bending part is formed to be inclined at a predetermined angle to the other side from the direction of fluid flow.

[0014] In addition, the first upper plate and the first lower plate are characterized in that a first inlet / outlet hole through which a first fluid flows in and out is formed at one end in the direction of fluid flow, and a second inlet / outlet hole through which a second fluid flows in and out is formed at each end in the direction of fluid flow.

[0015] Additionally, the first inlet / outlet hole is characterized in that it is formed on one edge of the first upper plate and the first lower plate.

[0016] In addition, the second inlet / outlet hole is characterized in that two or more are formed.

[0017] In addition, the second inlet / outlet hole is characterized in that at least one is formed along the perimeter of the first inlet / outlet hole.

[0018] In addition, the first bending portion and the second bending portion are connected to the second inlet / outlet hole, and the length of the bending part that is connected to the second inlet / outlet hole is shorter than the length of the bending part that is not connected to the second inlet / outlet hole.

[0019] In addition, the flow path includes a first flow path through which a first fluid flows and is located on the other surface of the first upper plate or the other surface of the first lower plate, and a second flow path through which a second fluid flows and is located between the first upper plate and the first lower plate, and the second flow path is formed by alternately arranging and connecting the bending parts of the first bending part and the bending parts of the second bending part, and the first flow path is formed in a U shape, with both ends connected to the first inlet / outlet hole, and the second flow path is formed in a straight shape, with both ends connected to the second inlet / outlet hole.

[0020] In addition, the second heat exchange part is characterized in that it includes at least one second upper plate and a second lower plate whose one side is in contact with each other to form a predetermined space therebetween, the second upper plate includes a third bent portion formed on one side to protrude toward the opposite side of the second lower plate, and the second lower plate includes a fourth bent portion formed on one side to protrude toward the opposite side of the second upper plate.

[0021] In addition, the third bending portion and the fourth bending portion include two or more predetermined bending parts that are formed to extend in a predetermined direction, and both ends of each bending part included in the third bending portion correspond to both ends of each bending part included in the fourth bending portion and are connected to each other.

[0022] In addition, each bending part is characterized by being formed by extending in a diagonal direction that forms a predetermined angle rather than being vertical or horizontal to the direction of fluid flow.

[0023] In addition, the bending part included in the third bending part is formed to be inclined at a predetermined angle to one side from the direction of fluid flow, and the bending part included in the fourth bending part is formed to be inclined at a predetermined angle to the other side from the direction of fluid flow.

[0024] In addition, the second upper plate and the second lower plate are characterized in that a third inlet / outlet hole through which the first fluid flows in and out and a fourth inlet / outlet hole through which the second fluid flows in and out are formed at one end in the direction of fluid flow.

[0025] Additionally, the third inlet / outlet hole is characterized in that it is formed on one edge of the second upper plate and the second lower plate.

[0026] In addition, the fourth inlet / outlet hole is characterized by being formed in two or more numbers.

[0027] In addition, the second inlet / outlet hole is characterized in that at least one is formed along the perimeter of the first inlet / outlet hole.

[0028] In addition, the third bending portion and the fourth bending portion are connected to the fourth inlet / outlet hole, and the length of the bending part that is connected to the fourth inlet / outlet hole is shorter than the length of the bending part that is not connected to the fourth inlet / outlet hole.

[0029] In addition, the euro portion includes a third euro formed on the other surface of the second upper plate or the other surface of the second lower plate, through which the first fluid flows, and a fourth euro formed between the second upper plate and the second lower plate, through which the second fluid flows, and the fourth euro formed by alternately arranging and connecting the bending parts of the third bending part and the bending parts of the fourth bending part, and the third euro and the fourth euro are formed in a U shape, and are characterized in that both ends are connected to the third inlet / outlet hole and the fourth inlet / outlet hole, respectively.

[0030]

[0031] The plate heat exchanger of the present invention having the above-described configuration has been devised to solve the above-described problems, and the purpose of the present invention is to form the flow paths through which the refrigerant flows in an alternating manner from top to bottom, thereby minimizing the cross-sectional area of ​​the flow path, thereby having the effect of satisfying high pressure resistance performance.

[0032] In addition, by forming the inlet and outlet of the refrigerant and cooling water so that they are tilted toward the corner ends, the shape of the bead that controls the flow of the cooling water and the heat exchange area are maximized, the cooling water dead volume is minimized, and the refrigerant flow area is maximized.

[0033]

[0034] Figure 1 is an exploded perspective view of the plate heat exchanger of the present invention.

[0035] Figure 2 is a schematic diagram illustrating the flow of a second fluid in a plate heat exchanger of the present invention.

[0036] Figure 3 is a schematic diagram illustrating the flow of a first fluid in a plate heat exchanger of the present invention.

[0037] Figure 4 is a schematic diagram showing the first bending portion and the second bending portion of the present invention.

[0038] Figure 5 is a cross-sectional view showing the first bending portion and the second bending portion of the present invention.

[0039] Figure 6 is a partial perspective view showing the first bending portion and the second bending portion of the present invention.

[0040] Figure 7 is a plan view showing the first upper plate and the first lower plate of the present invention overlapping.

[0041] Figure 8 is a schematic diagram illustrating the flow of a second fluid in the first heat exchange part of the present invention.

[0042] Figure 9 is a schematic diagram illustrating the flow of a first fluid in the first heat exchange part of the present invention.

[0043] Figure 10 is a schematic diagram showing the third bending portion and the fourth bending portion of the present invention.

[0044] Fig. 11 is a cross-sectional view showing the third bending portion and the fourth bending portion of the present invention.

[0045] Fig. 12 is a partial perspective view showing the third bending portion and the fourth bending portion of the present invention.

[0046] Figure 13 is a plan view showing the second upper plate and the second lower plate of the present invention overlapping each other.

[0047] Figure 14 is a schematic diagram illustrating the flow of a second fluid in a second heat exchange part of the present invention.

[0048] Figure 15 is a schematic diagram illustrating the flow of the first fluid in the second heat exchange part of the present invention.

[0049]

[0050] Hereinafter, the technical concept of the present invention will be described in more detail using the attached drawings. Prior to this, it should be noted that the terms and words used in this specification and claims should not be construed as limited to their conventional or dictionary meanings. Based on the principle that the inventor can appropriately define the concept of a term to best explain his or her invention, they should be interpreted in a way that aligns with the technical concept of the present invention.

[0051]

[0052] Hereinafter, the basic configuration of the plate heat exchanger (1000) of the present invention will be described with reference to FIGS. 1 to 3.

[0053] As illustrated in FIG. 1, the plate heat exchanger (1000) of the present invention may include a heat exchange part (100) that exchanges heat between a first fluid (F1) and a second fluid (F2), including at least one first heat exchange part (110) and a second heat exchange part (120) that are laminated in a predetermined lamination direction and a flow path (130) through which a predetermined first fluid (F1) or a second fluid (F2) flows. In this case, the first fluid (F1) may be a cooling water, and the second fluid (F2) may be a refrigerant that cools the first fluid (F1). The first heat exchange part (110) and the second heat exchange part (120) may be configured independently of each other, and a supporting or insulating plate may be further laminated between the first heat exchange part (110) and the second heat exchange part (120).

[0054] At this time, the first heat exchange part (110) and the second heat exchange part (120) may include a plurality of plates that are stacked in a stacking direction, and the flow path (130) may be formed by bending at least one of the plates. That is, the injected first fluid (F1) and second fluid (F2) can flow between each of the plates included in the first heat exchange part (110) and the second heat exchange part (120), and a structure may be adopted for increasing the pressure inside the flow path (130) through which the first fluid (F1) and the second fluid (F2) flow by simply changing the shape of each plate without adding a separate part to satisfy the internal pressure requirement. Accordingly, even if R744, which is an environmentally friendly refrigerant, is applied to the second fluid (F2), the second fluid (F2) can flow under a constant pressure when flowing in the heat exchange part (100) of the present invention, and the temperature of the second fluid (F2) can be maintained low.

[0055] In addition, the plate heat exchanger (1000) of the present invention may include an end plate (200) in the shape of a plate that is laminated in a stacking direction on one side of a first heat exchange part (110), a first manifold (300) coupled to one end of the end plate (200) in a predetermined fluid flow direction and into which a first fluid (F1) is introduced and discharged, and a second manifold (400) coupled to the other end of the end plate (200) in the fluid flow direction and into which a second fluid (F2) is introduced and discharged. The first manifold (300) and the second manifold may be formed close to each of the two ends of the end plate (200), that is, at corners that face each other, thereby maximizing the surface area through which the first fluid (F1) and the second fluid (F2) transfer heat, and minimizing the dead volume when the first fluid (F1) flows.

[0056] At this time, as illustrated in FIG. 2, the second fluid (F2), i.e., the refrigerant, injected by the second manifold (400) is first injected into the first heat exchange part (110), then moves to the second heat exchange part (120), and then rotates in the second heat exchange part (120) and can be discharged to the outside again. Accordingly, both the first heat exchange part (110) and the second heat exchange part (120) can come into contact with the first fluid (F1) and perform heat exchange, respectively.

[0057] In addition, as illustrated in FIG. 3, the first fluid (F1), i.e., the cooling water, injected by the first manifold (300) is injected in a direction perpendicular to the stacking direction and can be injected in parallel to the first heat exchange part (110) and the second heat exchange part (120), respectively. Each cooling water can exchange heat with the second fluid (F2) in the first heat exchange part (110) and the second heat exchange part (120) and then be circulated and discharged to the outside through the first manifold (300).

[0058] By including at least one first heat exchange part (110) and a second heat exchange part (120) that are independently arranged in this way, the area where the first fluid (F1) and the second fluid (F2) exchange heat can be increased, and at the same time, the amount of the first fluid (F1) that is heat-exchanged can be increased. In other words, the heat exchange efficiency can be increased.

[0059]

[0060] Hereinafter, the first heat exchange part (110) of the present invention will be described in more detail with reference to FIGS. 4 to 9.

[0061] As illustrated in FIGS. 4 to 6, the first heat exchange part (110) may include at least one first upper plate (111) and one first lower plate (112) having one surface in contact with each other to form a predetermined space therebetween. At this time, the first upper plate (111) may include a first bent portion (111a) formed on one surface to protrude toward the opposite side of the first lower plate (112), and the first lower plate (112) may include a second bent portion (112a) formed on one surface to protrude toward the opposite side of the first upper plate (111). Accordingly, a high-pressure side working fluid path may be formed, thereby ensuring high-pressure durability.

[0062] The first bend portion (111a) and the second bend portion (112a) can be formed to have the same thickness as the area where the first bend portion (111a) and the second bend portion (112a) are not formed, and accordingly, the surfaces facing each other can be formed concavely as they protrude toward opposite sides of each other, so that a space can be formed therebetween. The second fluid (F2) described above can flow through this space. At this time, the first fluid (F1) can flow to the other side of the first upper plate (111) and the first lower plate (112). That is, the first fluid (F1) can flow to the side where either the first bend part or the second bend part formed on the first upper plate (111) and the first lower plate (112) protrudes, and the flow can be controlled. Details will be described later.

[0063] At this time, the first bending portion (111a) and the second bending portion (112a) include two or more predetermined bending parts that extend in a predetermined direction, and both ends of each of the bending parts included in the first bending portion (111a) correspond to both ends of each of the bending parts included in the second bending portion (112a) and can be connected to each other. At this time, the average cross-sectional area of ​​the flow path (the second flow path (132) in the paragraph to be described later) of the second fluid (F2) formed by the first bending portion (111a) and the second bending portion (112a) can be less than 2㎟. Accordingly, the required pressure resistance performance can be satisfied so that the temperature of the second fluid (F2) is maintained.

[0064] In addition, as illustrated in FIG. 7, each bending part may be formed to extend in a diagonal direction that is not vertical or horizontal to the direction of fluid flow but rather forms a predetermined angle. In addition, the bending part included in the first bending portion (111a) may be formed to be inclined to form a predetermined angle to one side from the direction of fluid flow, and the bending part included in the second bending portion (112a) may be formed to be inclined to form a predetermined angle to the other side from the direction of fluid flow. In this way, the bending parts formed on the first upper plate (111) and the first lower plate (112) are formed to be staggered, so that the flow of the first fluid (F1) flowing in contact with the other surface of the first upper plate (111) and the flow of the first fluid (F1) flowing in contact with the other surface of the first lower plate (112) can be staggered, and the first fluid (F1) and the second fluid (F2) can exchange heat more evenly.

[0065] In addition, the first upper plate (111) and the first lower plate (112) may have a first inlet / outlet hole (113) formed at one end in the fluid flow direction, which communicates with the first manifold (300), and two or more second inlet / outlet holes (114) formed at each end in the fluid flow direction, which communicate with the second manifold (400). The second inlet / outlet holes (114) may have a smaller diameter than the first inlet / outlet holes (113), and two or more second inlet / outlet holes (114) may be formed at each end of the first upper plate (111) and the second lower plate (122). Accordingly, the heat transfer surface area may be maximized.

[0066] At this time, the first inlet / outlet hole (113) can be formed on one edge of the first upper plate (111) and the first lower plate (112), and the second inlet / outlet holes (114) can be arranged at a predetermined distance from each other along the periphery of the first inlet / outlet hole (113).

[0067] In addition, the first bend (111a) and the second bend (112a) can be connected to the second inlet / outlet hole (114). At this time, the bend parts of the first bend (111a) and the second bend (112a) can be connected to one second inlet / outlet hole (114), and the bend parts of the first bend (111a) and the second bend (112a) connected to one second inlet / outlet hole (114) can be connected to and branched into two independent second flow paths (132). That is, the second fluid (F2) injected into one second inlet / outlet hole (114) can flow by branching into two, thereby maximizing the heat transfer surface area and preventing the second flow path (132) from being blocked.

[0068] In addition, the length of the folded part that is connected to the second inlet / outlet hole (114) may be shorter than the length of the folded part that is not connected to the second inlet / outlet hole (114). Accordingly, the pressure resistance performance and packageability of the first heat exchange part (110) can be secured.

[0069] To explain more clearly, as illustrated in FIG. 8, the flow path (130) includes a second flow path (132) located between the first upper plate (111) and the first lower plate (112), through which the second fluid (F2) flows, and the second flow path (132) may be formed by alternately arranging and connecting the bending parts of the first bending portion (111a) and the bending parts of the second bending portion (112a). Accordingly, the second flow path (132) may be formed in a zigzag shape, but may be formed so that the overall flow direction of the second fluid (F2) is straight. In addition, the second flow path (132) may be connected at both ends to the second inlet / outlet holes (114), and two may be connected to one second inlet / outlet hole (114). At this time, the two second flow paths (132) connected to one second inlet / outlet hole (114) may have opposite zigzag directions. Accordingly, the second fluid (F2) injected into one second inlet / outlet hole (114) may branch out and flow, thereby maximizing the heat transfer surface area and preventing the second flow path (132) from becoming blocked.

[0070] As illustrated in FIG. 9, the flow path (130) may include a first flow path (131) through which a first fluid (F1) flows and which is positioned on the other surface of the first upper plate (111) or the other surface of the first lower plate (112), and the first flow path (131) may be formed in a U shape. Accordingly, the first fluid (F1) flowing in the first flow path (131) may exchange heat with the second fluid (F2) flowing in the second flow path (132), and may rotate and move back toward the first manifold (300) or the second heat exchange part (120). In addition, since the bending parts formed on the first upper plate (111) and the first lower plate (112) are formed to be staggered, the flow directions of the first fluid (F1) flowing in contact with the other surface of the first upper plate (111) and the first fluid (F1) flowing in contact with the other surface of the first lower plate (112) can be different from each other, and the heat transfer surface area in contact with the second fluid (F2) can be maximized, thereby increasing the heat exchange efficiency.

[0071]

[0072] Hereinafter, the second heat exchange part (120) of the present invention will be described in more detail with reference to FIGS. 10 to 15.

[0073] As illustrated in FIGS. 10 to 12, the second heat exchange part (120) may include at least one second upper plate (121) and a second lower plate (122) whose surfaces are in contact with each other to form a predetermined space therebetween. At this time, the second upper plate (121) may include a third bent portion (121a) formed by bending on one surface to protrude toward the opposite side of the second lower plate (122), and the second lower plate (122) may include a fourth bent portion (122a) formed by bending on one surface to protrude toward the opposite side of the second upper plate (121).

[0074] The third bend portion (121a) and the fourth bend portion (122a) can be formed to have the same thickness as the area where the third bend portion (121a) and the fourth bend portion (122a) are not formed, and accordingly, the surfaces facing each other can be formed concavely as they protrude toward opposite sides of each other, so that a space can be formed therebetween. The second fluid (F2) described above can flow through this space. At this time, the first fluid (F1) can flow to the other surface of the second upper plate (121) and the second lower plate (122). That is, the first fluid (F1) can flow to the side where either the first bend part or the second bend part formed on the second upper plate (121) and the second lower plate (122) protrudes, and the flow can be controlled. Details will be described later.

[0075] At this time, the third bending portion (121a) and the fourth bending portion (122a) include two or more predetermined bending parts that extend in a predetermined direction, and both ends of each of the bending parts included in the third bending portion (121a) correspond to both ends of each of the bending parts included in the fourth bending portion (122a) and can be connected to each other. At this time, the average cross-sectional area of ​​the flow path (the fourth flow path (134) in the paragraph to be described later) of the second fluid (F2) formed by the third bending portion (121a) and the fourth bending portion (122a) can be less than 2㎟. Accordingly, the required pressure resistance performance can be satisfied so that the temperature of the second fluid (F2) is maintained.

[0076] In addition, as illustrated in FIG. 13, each of the bending parts may be formed to extend in a diagonal direction that is not vertical or horizontal to the direction of fluid flow but rather forms a predetermined angle. In addition, the bending part included in the third bending part (121a) may be formed to be inclined to form a predetermined angle to one side from the direction of fluid flow, and the bending part included in the fourth bending part (122a) may be formed to be inclined to form a predetermined angle to the other side from the direction of fluid flow. In this way, the bending parts formed on the second upper plate (121) and the second lower plate (122) are formed to be staggered, so that the flow of the first fluid (F1) flowing in contact with the other surface of the second upper plate (121) and the flow of the first fluid (F1) flowing in contact with the other surface of the second lower plate (122) can be staggered, and the first fluid (F1) and the second fluid (F2) can exchange heat more evenly.

[0077] In addition, the second upper plate (121) and the second lower plate (122) may have a third inlet / outlet hole (123) formed at one end in the fluid flow direction, which communicates with the first manifold (300), and two or more fourth inlet / outlet holes (124) formed at one end in the fluid flow direction, which communicate with the second manifold (400). The fourth inlet / outlet hole (124) may have a smaller diameter than the third inlet / outlet hole (123), and two or more fourth inlet / outlet holes (124) may be formed in a row at one end of the second upper plate (121) and the second lower plate (122). Accordingly, the heat transfer surface area may be maximized.

[0078] At this time, the third inlet / outlet hole (123) can be formed on one edge of the second upper plate (121) and the second lower plate (122), and the fourth inlet / outlet hole (124) can be arranged at a predetermined interval from each other along the periphery of the third inlet / outlet hole (123).

[0079] In addition, the third bend (121a) and the fourth bend (122a) can be connected to the fourth inlet / outlet hole (124). At this time, the bend parts of the third bend (121a) and the fourth bend (122a) can be connected to one fourth inlet / outlet hole (124), and the bend parts of the third bend (121a) and the fourth bend (122a) connected to one fourth inlet / outlet hole (124) can be connected to and branched into two independent fourth flow paths (134). That is, the second fluid (F2) injected into one fourth inlet / outlet hole (124) can flow by branching into two, thereby maximizing the heat transfer surface area and preventing the fourth flow path (134) from being blocked.

[0080] Additionally, the length of the folded part that is connected to the fourth inlet / outlet hole (124) may be shorter than the length of the folded part that is not connected to the fourth inlet / outlet hole (124). Accordingly, the pressure resistance performance and packageability of the second heat exchange part (120) can be secured.

[0081] To explain more clearly, as illustrated in FIG. 14, the flow path (130) includes a fourth flow path (134) located between the second upper plate (121) and the second lower plate (122), through which the second fluid (F2) flows, and the fourth flow path (134) may be formed by alternately arranging and connecting the bending parts of the third bending part (121a) and the bending parts of the fourth bending part (122a). Accordingly, the fourth flow path (134) may be formed in a zigzag shape, but may be formed such that the overall flow direction of the second fluid (F2) turns in a U shape. At this time, the fourth inlet / outlet hole (124) through which the second fluid (F2) flows in may be different from the fourth inlet / outlet hole (124) through which the second fluid (F2) flows out. In addition, the fourth flow path (134) is connected to the fourth inlet / outlet hole (124) at both ends, and two flow paths can be connected to one fourth flow path (124). At this time, the two fourth flow paths (134) connected to one fourth flow path (124) can have opposite zigzag directions. Accordingly, the second fluid (F2) injected into one fourth flow path (124) can flow in two branches, thereby maximizing the heat transfer surface area and preventing the fourth flow path (134) from being blocked.

[0082] As illustrated in FIG. 15, the flow path (130) may include a third flow path (133) through which a first fluid (F1) flows and which is located on the other surface of the second upper plate (121) or the other surface of the second lower plate (122), and the third flow path (133) may be formed in a U shape. Accordingly, the first fluid (F1) flowing in the third flow path (133) may exchange heat with the second fluid (F2) flowing in the fourth flow path (134), and may rotate and move back toward the first manifold (300) or the first heat exchange part (110). In addition, since the bending parts formed on the second upper plate (121) and the second lower plate (122) are formed to be staggered, the flow directions of the first fluid (F1) flowing in contact with the other surface of the second upper plate (121) and the first fluid (F1) flowing in contact with the other surface of the second lower plate (122) can be different from each other, and the heat transfer surface area in contact with the second fluid (F2) can be maximized, thereby increasing the heat exchange efficiency.

[0083]

[0084] The technical concept of the present invention should not be construed solely based on the above-described embodiments. The scope of application is diverse, and various modifications and variations are possible within the scope of those skilled in the art without departing from the spirit of the invention as claimed in the claims. Therefore, such improvements and modifications, as long as they are obvious to those skilled in the art, fall within the scope of protection of the present invention.

[0085]

[0086] [Explanation of symbols]

[0087] 1000: Plate heat exchanger

[0088] 100: Heat exchanger

[0089] 110: First heat exchange part

[0090] 111: First top plate

[0091] 111a: First bend

[0092] 112: First lower plate

[0093] 112a: Second bend

[0094] 113: First inlet / outlet hole

[0095] 114: Second inlet / outlet hole

[0096] 120: Second heat exchange part

[0097] 121: Second top plate

[0098] 121a: Third bend

[0099] 122: Second lower plate

[0100] 122a: 4th bend

[0101] 123: Third inlet / outlet hole

[0102] 124: 4th inlet / outlet hole

[0103] 130: Eurozone

[0104] 131: 1st Euro

[0105] 132: Second Euro

[0106] 133: Third Euro

[0107] 134: 4th Euro

[0108] 200: End Plate

[0109] 300: 1st manifold

[0110] 400: Second manifold

[0111] F1: First fluid

[0112] F2: Second fluid

Claims

1. A heat exchange unit including a first heat exchange part and a second heat exchange part laminated in a predetermined lamination direction and a flow path through which a predetermined first fluid or second fluid flows, for heat exchange between the first fluid and the second fluid; An end plate in the shape of a plate laminated in the lamination direction on one side of the first heat exchange part; Including, The above first heat exchange part and the above second heat exchange part, It comprises a plurality of plates laminated in the above lamination direction, A plate heat exchanger characterized in that the above-mentioned euro portion forms a passage for a working fluid by forming at least one of the plates by bending.

2. In paragraph 1, The above first heat exchange part, It comprises at least one first upper plate and one first lower plate, each of which has one side in contact with the other to form a predetermined space therebetween, The first upper plate includes a first bent portion formed on one side thereof so as to protrude toward the opposite side of the first lower plate, A plate heat exchanger, characterized in that the first lower plate includes a second bent portion formed on one side thereof so as to protrude toward the opposite side of the first upper plate.

3. In paragraph 2, The above first bend portion and the above second bend portion Contains two or more predetermined bending parts that are formed by extending in a predetermined direction, A plate heat exchanger, characterized in that both ends of each of the above-mentioned folded parts included in the above-mentioned first folded section correspond to both ends of each of the above-mentioned folded parts included in the above-mentioned second folded section and are connected to each other.

4. In paragraph 3, Each of the above bending parts, A plate heat exchanger characterized by being formed by extending in a diagonal direction that forms a predetermined angle, rather than being vertical or horizontal, with respect to a predetermined fluid flow direction.

5. In paragraph 4, The bending part included in the first bending section is formed so as to be inclined at a predetermined angle to one side from the direction of flow of the fluid, A plate heat exchanger, characterized in that the bending part included in the second bending section is formed to be inclined at a predetermined angle to the other side from the direction of flow of the fluid.

6. In paragraph 3, The above first upper plate and the above first lower plate A first inlet / outlet hole is formed at one end of a predetermined fluid flow direction through which the first fluid flows in and out, A plate heat exchanger characterized in that second inlet / outlet holes through which the second fluid flows in and out are formed at each end of the fluid flow direction.

7. In paragraph 6, The above first inlet / outlet hole is, A plate heat exchanger characterized in that it is formed on one side edge of the first upper plate and the first lower plate.

8. In paragraph 6, The above second inlet / outlet hole is, A plate heat exchanger characterized by being formed of two or more.

9. In paragraph 6, The above second inlet / outlet hole is, A plate heat exchanger characterized in that at least one is formed along the periphery of the first inlet / outlet hole.

10. In paragraph 6, A plate heat exchanger, wherein the first bend portion and the second bend portion are connected to the second inlet / outlet hole, and the length of the bend portion that is connected to the second inlet / outlet hole is shorter than the length of the bend portion that is not connected to the second inlet / outlet hole.

11. In paragraph 6, The above Euro part, A first flow path through which the first fluid flows and which is located on the other surface of the first upper plate or the other surface of the first lower plate; The second fluid flows through a second passage located between the first upper plate and the first lower plate, The above second euro is formed by alternately arranging and connecting the bending part of the first bending part and the bending part of the second bending part, The above first euro is formed in a U shape, and both ends are connected to the first inlet and outlet holes. A plate heat exchanger, characterized in that the second euro is formed in a straight line and both ends are connected to the second inlet and outlet holes.

12. In paragraph 1, The above second heat exchange part, It comprises at least one second upper plate and one second lower plate, each of which has one side in contact with the other to form a predetermined space therebetween, The second upper plate includes a third folded portion formed on one side thereof so as to protrude toward the opposite side of the second lower plate, A plate heat exchanger, characterized in that the second lower plate includes a fourth bent portion formed on one side thereof so as to protrude toward the opposite side of the second upper plate.

13. In paragraph 12, The above third bend and the above fourth bend Contains two or more predetermined bending parts that are formed by extending in a predetermined direction, A plate heat exchanger, characterized in that both ends of each of the above-mentioned folded parts included in the above-mentioned third folded section correspond to both ends of each of the above-mentioned folded parts included in the above-mentioned fourth folded section and are connected to each other.

14. In paragraph 9, Each of the above bending parts, A plate heat exchanger characterized by being formed by extending in a diagonal direction that forms a predetermined angle, not vertical or horizontal, with respect to the direction in which the fluid flows.

15. In paragraph 13, The above-mentioned bending part included in the third bending section is formed by being inclined to form a predetermined angle to one side from a predetermined fluid flow direction, A plate heat exchanger, characterized in that the bending part included in the fourth bending section is formed to be inclined at a predetermined angle to the other side from the direction of fluid flow.

16. In paragraph 13, The above second upper plate and the above second lower plate A plate heat exchanger characterized in that a third inlet / outlet hole through which the first fluid flows in and out and a fourth inlet / outlet hole through which the second fluid flows in and out are formed at one end in a predetermined fluid flow direction.

17. In paragraph 16, The above third inlet / outlet hole is, A plate heat exchanger characterized in that it is formed on one side edge of the second upper plate and the second lower plate.

18. In paragraph 16, The above fourth inlet / outlet hole is, A plate heat exchanger characterized by being formed of two or more.

19. In paragraph 16, The above fourth inlet / outlet hole is, A plate heat exchanger characterized in that at least one is formed along the periphery of the third inlet / outlet hole.

20. In paragraph 16, A plate heat exchanger, characterized in that the third bend portion and the fourth bend portion are connected to the fourth inlet / outlet hole, and the length of the bend part that is connected to the fourth inlet / outlet hole is shorter than the length of the bend part that is not connected to the fourth inlet / outlet hole.

21. In paragraph 16, The above Euro part, The first fluid flows, and a third flow path formed on the other surface of the second upper plate or the other surface of the second lower plate, The second fluid flows and includes a fourth passage formed between the second upper plate and the second lower plate, The above fourth euro is formed by alternately arranging and connecting the bending part of the third bending part and the bending part of the fourth bending part, A plate heat exchanger, characterized in that the third and fourth euros are formed in a U shape and both ends are connected to the third inlet and outlet hole and the fourth inlet and outlet hole, respectively.

Images