Heat exchanger

Abstract

A heat exchanger according to the present application includes a plate having an inlet port and a first merging port on one side thereof through which a fluid flows in, a periphery of the first merging port being projected upward, and a discharge port and a second merging port on the other side thereof through which a fluid is discharged, a periphery of the second merging port being projected upward, and a heat radiating fin located on an upper surface of the plate and having at least one non-heat radiating fin portion having a specific area cut in a direction parallel to a direction from one side to the other side of the plate. The heat radiating fin can be inserted between a pair of stacked plates.

Description

Technical Field

[0001] The present invention relates to a heat exchanger, and more specifically, to a heat exchanger having a bypass flow path formed to prevent pressure loss of fluid flowing in the plate. Background Technology

[0002] Generally, a heat exchanger is a device designed to allow two or more fluids to exchange heat with each other. Heat exchangers are used to allow different fluids to exchange heat, thereby cooling or heating the fluids. Typically, heat exchangers are used in vehicle cooling / heating systems, refrigerators, air conditioners, etc.

[0003] Typically, plate heat exchangers used in vehicle cooling / heating systems have channels formed between plates, each plate having a predetermined thickness, allowing fluid to flow through the channels. The plate heat exchanger is characterized by multiple plates arranged at predetermined intervals, allowing different fluids to flow alternately through the channels between the plates.

[0004] Referring to Korean Patent Application Publication No. 10-2020-0011163, such as Figure 1 As shown, a water-cooled condenser 1, which is one of the heat exchangers, may have multiple stacked plates 10 to define the flow section through which the fluid flows.

[0005] Referring to Korean Patent No. 10-1206858, such as Figure 2 As shown, the plate-shaped heat exchange unit 30 in the prior art may include a fluid inlet / outlet portion, which includes a first fluid inlet port 11, a first fluid outlet port 12, a second fluid inlet port 21, and a second fluid outlet port 22. Furthermore, a first pressure enhancement structure 41 and a second pressure enhancement structure 42 may be disposed in a region adjacent to the fluid inlet / outlet portion. The heat exchange unit may include a plate 51 and a herringbone section 50, the herringbone section 50 being configured to dissipate heat from the fluid while exchanging heat with it.

[0006] In other words, existing plate heat exchangers use heat dissipation components such as herringbone sections or heat dissipation fins to dissipate heat from the fluid flowing between the plates. Using herringbone sections and heat dissipation fins improves the heat exchanger's heat dissipation performance. However, when the shape of the herringbone section or heat dissipation fins is perpendicular to the fluid flow, it can sometimes lead to adverse effects such as excessive fluid pressure loss.

[0007] [Related Technical Documents]

[0008] [Patent Literature]

[0009] Korean Patent Application Publication No. 10-2020-0011163 (published on February 3, 2020)

[0010] Korean Patent No. 10-1206858 (registered on November 26, 2012) Summary of the Invention

[0011] Technical issues

[0012] The present invention aims to solve the above-mentioned problems, and the object of the present invention is to provide a heat exchanger in which a portion of the heat dissipation fins inserted into a stacked plate are cut off, which makes it possible to prevent pressure loss of the fluid flowing in the stacked plate.

[0013] Technical solution

[0014] The heat exchanger according to the invention may include: plates, each plate having an inlet port for introducing fluid and an outlet port for discharging said fluid; and heat dissipation fins inserted between a pair of plates, wherein the inlet port and the outlet port are formed on one side based on the width direction of the plates and spaced apart from each other in the longitudinal direction of the plates, wherein the heat dissipation fins include non-heat dissipation fin portions formed on the other side based on the width direction of the plates, and wherein a heat exchanger core is formed by stacking a plurality of plates.

[0015] In addition, the non-heat-dissipating fin portion can be formed by cutting a portion of the heat-dissipating fins.

[0016] Furthermore, the plate may include: a first connector port having an upwardly projecting periphery; and a second connector port having an upwardly projecting periphery, wherein the first connector port and the second connector port may be formed on the other side based on the width direction of the plate and spaced apart from each other in the longitudinal direction of the plate.

[0017] In this configuration, the heat dissipation fins may have holes formed corresponding to the inlet port, the outlet port, the first connector port, and the second connector port, and the heat dissipation fins are located on the upper surface of the plate.

[0018] Furthermore, the non-heat dissipation fin portion can be formed within the maximum distance range between the outer diameter of the first connector port and the outer diameter of the second connector port, and positioned at the edge of the heat dissipation fin.

[0019] Furthermore, the non-heat dissipation fin portion can be configured to include the point furthest from both the inlet port and the outlet port.

[0020] Furthermore, the cutting start point of the non-heat dissipation fin portion can be located at a point corresponding to the outer diameter range of the first connector port, and the outer diameter range can be applied based on the direction parallel to the direction from one side of the plate to the other.

[0021] Furthermore, the cutting endpoint of the non-heat dissipation fin portion can be located at a point corresponding to the outer diameter range of the second connector port, and the outer diameter range can be applied based on the direction parallel to the direction from one side of the plate to the other.

[0022] Furthermore, the non-heat dissipation fin portion may have a width of 1 mm to 1.5 mm in the direction from the edge of the heat dissipation fin to the interior.

[0023] Furthermore, in the non-heat dissipation fin portion, the cutting width of the central portion can be greater than the cutting width at the starting point and the cutting width at the ending point.

[0024] Furthermore, in the non-heat dissipation fin portion, the cutting width at the starting point and the cutting width at the ending point can be different from each other.

[0025] In this case, in the non-heat dissipation fin portion, the cut width can be increased in the direction from the cut start point to the cut end point.

[0026] Furthermore, in the non-heat dissipation fin portion, the cutting width can be reduced in the direction from the cutting start point to the cutting end point.

[0027] According to the invention, a heat exchanger is provided, wherein a coolant flows through the heat exchanger core, and the heat exchanger further includes: a receiver dryer; and a connector configured to connect the heat exchanger core and the receiver dryer.

[0028] Beneficial effects

[0029] With the above-described construction, the heat exchanger according to the invention can maintain maximum performance in terms of heat dissipation from fluid flowing through the space defined by the stacked plates, and minimize pressure loss caused by the increased fluid flow path due to the shape of the heat dissipation fins. Attached Figure Description

[0030] Figure 1 This is an exploded perspective view of a water-cooled condenser in the prior art.

[0031] Figure 2 This is a 3D view of a heat exchanger plate in the prior art.

[0032] Figure 3 This is an exploded perspective view showing the stacked plate and heat dissipation fins according to the present invention.

[0033] Figure 4 This is a top view showing the assembly of the plate and heat dissipation fins according to the first embodiment of the present invention.

[0034] Figure 5 This is an enlarged view showing the plate and heat dissipation fins according to the first embodiment of the present invention.

[0035] Figure 6 This is a top view showing the assembly of the plate and heat dissipation fins according to a second embodiment of the present invention.

[0036] Figure 7 This is a top view showing the assembly of the plate and heat dissipation fins according to the third and fourth embodiments of the present invention.

[0037] Figure 8 This is a top view showing the assembly of the plate and heat dissipation fins according to the fifth and sixth embodiments of the present invention.

[0038] Figure 9 This is a perspective view showing a water-cooled condenser according to the present invention.

[0039] Figure 10 This is a graph representing the pressure loss (dP) and heat transfer coefficient (h) in response to changes in the outer diameter range A based on the cut width B.

[0040] Figure 11 This is a graph representing the pressure loss (dP) and heat transfer coefficient (h) in response to changes in the cut width B based on the outer diameter range A. Detailed Implementation

[0041] The technical spirit of the invention will be described in more detail below using the accompanying drawings. Furthermore, the terms or words used in the specification and claims should not be construed as limited to their general or dictionary meanings, but rather as meanings and concepts consistent with the technical spirit of the invention, based on the inventor's ability to appropriately define the concepts of the terms in order to best describe the principles of his / her own invention. Therefore, the exemplary embodiments disclosed in this specification and the constructions shown in the accompanying drawings are merely preferred exemplary embodiments of the invention and do not represent the full technical spirit of the invention. Therefore, it should be understood that various modifications can be made to replace the exemplary embodiments at the time of filing this application.

[0042] The technical spirit of the invention will be described in more detail below using the accompanying drawings. The drawings are merely exemplary embodiments shown to illustrate the technical spirit of the invention in more detail, and the technical spirit of the invention is not limited to the form of the drawings.

[0043] See Figure 3 and Figure 4The heat exchanger according to the invention may include: plates 100, each plate having an inlet port 110 for introducing fluid and an outlet port 120 for discharging fluid therefrom; and heat dissipation fins 200 inserted between a pair of plates 100a and 100b. The inlet port 110 and outlet port 120 may be formed on one side based on the width direction of the plates 100 and spaced apart from each other in the longitudinal direction of the plates 100. The heat dissipation fins 200 may include non-heat dissipation fin portions 210 formed on the other side based on the width direction of the plates 100. A plurality of plates 100 may be stacked to define a heat exchanger core.

[0044] The fluid flowing through the space defined by the stacked plates 100a and 100b can be oil or coolant. However, the type of fluid is not limited. The fluid can be introduced into inlet port 110, flow through the space between the plates 100a and 100b, and be discharged to outlet port 120. A partition wall is formed around the plates 100 to prevent fluid leakage to the outside of the plates 100.

[0045] The heat dissipation fins 200 have a shape in which horizontal structures relative to the direction of fluid flow and structures perpendicular to the direction of fluid flow are repeatedly coupled, thereby improving the heat dissipation effect of the fluid flowing through the space between a pair of plates 100a and 100b.

[0046] The non-heat dissipation fin portion 210 can be formed by cutting a portion of the heat dissipation fin 200 and is located on the other side of the width direction of the base plate 100.

[0047] Furthermore, the plate 100 may include a first connector port 130 having an upwardly projecting periphery and a second connector port 140 having an upwardly projecting periphery. The first connector port 130 and the second connector port 140 may be formed on the opposite side based on the width direction of the plate 100 and spaced apart from each other in the longitudinal direction of the plate 100.

[0048] like Figure 4 As shown, the plates 100a and 100b can be stacked such that the second connector port 140 of the upper plate 100b is positioned above the inlet port 110 of the lower plate 100a, the first connector port 130 of the upper plate 100b is positioned above the outlet port 120 of the lower plate 100a, the outlet port 120 of the upper plate 100b is positioned above the first connector port 130 of the lower plate 100a, and the inlet port 110 of the upper plate 100b is positioned above the second connector port 140 of the lower plate 100a.

[0049] With the plates 100a and 100b stacked, the peripheries of the first connector port 130 and the second connector port 140 protrude, thereby physically separating them from the inlet port 110, the outlet port 120, and the space between the plates 100a and 100b. Heat dissipation fins 200 are inserted into the space between the plates 100a and 100b, thus fixing the position of the heat dissipation fins 200.

[0050] Furthermore, the heat dissipation fins 200 may have holes 220 corresponding to the inlet port 110, outlet port 120, first connector port 130, and second connector port 140, and are located on the upper surface of the plate 100. That is, the heat dissipation fins 200 may be located on the upper surface of the plate 100 and have holes 220 that correspond in size and position to the inlet port 110, outlet port 120, first connector port 130, and second connector port 140 formed in the plate 100. Therefore, obstruction to fluid flow can be minimized, the overall performance of heat dissipation from the fluid can be improved, and the deterioration of the coupling force between the pair of plates 100a and 100b can be prevented.

[0051] The shape of the heat dissipation fins 200, which have a structure perpendicular to the flow direction, increases the flow distance of the fluid, which may lead to pressure loss. Therefore, in order to minimize pressure loss, the heat dissipation fins 200 according to the invention include a non-heat dissipation fin portion 210, so that the fluid can bypass the heat dissipation fins 200 and move toward the outlet port 120 without receiving resistance.

[0052] In this case, a non-heat-dissipating fin portion 210 is formed by cutting a portion of the heat dissipating fin 200. The non-heat-dissipating fin portion 210 refers to the space formed by machining (cutting) a portion of the heat dissipating fin 200 or bending a portion of the heat dissipating fin 200 in a direction perpendicular to the surface direction of the heat dissipating fin 200 so that the heat dissipating fin 200 is not formed.

[0053] Therefore, the heat exchanger according to the invention can maintain maximum performance in terms of heat dissipation from fluid flowing through the space defined by the stacked plates 100a and 100b, and minimize pressure loss caused by the increased fluid flow path due to the shape of the heat dissipation fins 200.

[0054] Reference Figure 4In this invention, the straight line connecting the center of the inlet port 110 and the center of the outlet port 120 can be parallel to the straight line connecting the center of the first connector port 130 and the center of the second connector port 140. That is, the center of the inlet port 110 and the center of the outlet port 120 can be located on the same straight line, and the center of the first connector port 130 and the center of the second connector port 140 can also be located on the same straight line. The two straight lines can be parallel to each other, and the two straight lines can be parallel to the direction from one side of the plate 100 to the other.

[0055] Furthermore, the non-heat dissipation fin portion 210 can be formed within the maximum distance range between the outer diameters of the first connector port 130 and the second connector port 140, and is positioned at the edge of the heat dissipation fin 200. That is, the two opposite ends (cutting start point and cutting end point) of the non-heat dissipation fin portion 210 can be positioned within the maximum distance range between the outer diameters of the first connector port 130 and the second connector port 140, and are positioned at the edge of the heat dissipation fin 200, i.e., at the edge. The edge of the heat dissipation fin 200 is a region where the obstruction to fluid flow caused by the heat dissipation fin 200 is minimal, and the fluid flow velocity is highest. Therefore, when the non-heat dissipation fin portion 210 is positioned at the edge of the heat dissipation fin 200, the flow of fluid obstructed by the heat dissipation fin 200 can bypass the heat dissipation fin 200, maximizing the flow velocity of the fluid bypassing the heat dissipation fin 200 and thus minimizing pressure loss.

[0056] In this configuration, the non-heat-dissipating fin portion 210 may include the point furthest from both the inlet port 110 and the outlet port 120. That is, the non-heat-dissipating fin portion 210 may include the point on the heat-dissipating fin 200 furthest from both the inlet port 110 and the outlet port 120, specifically the point between the protrusions of the first connector port 130 and the second connector port 140. Therefore, the non-heat-dissipating fin portion 210 can be positioned in the region that exerts the highest degree of obstruction on fluid flow and allows fluid to bypass the heat-dissipating fin 200, thereby effectively preventing pressure loss.

[0057] Reference Figure 5 In the non-heat dissipation fin portion 210, the cutting start point S can be located at a point corresponding to the outer diameter range A of the first connector port 130, and the outer diameter based on the direction parallel to the direction from one side of the plate 100 to the other can be applied to the outer diameter range A.

[0058] Furthermore, in the non-heat dissipation fin portion 210, the cutting endpoint E can be located at a point corresponding to the outer diameter range A of the second connector port 140, and the outer diameter based on the direction parallel to the direction from one side of the plate 100 to the other can be applied to the outer diameter range A.

[0059] With the outer diameter of each of the first connector port 130 and the second connector port 140 being 22.4 mm, the performance analysis related to the cutting start point S, cutting end point E, and cutting width B of the non-heat dissipation fin portion 210 will be described below.

[0060] As shown in Table 1, when the outer diameter range A is 0 mm to 22.4 mm and a cutting width B of 0.5 mm to 2.5 mm is applied,

[0061] [Table 1]

[0062]

[0063] Can obtain Figure 10 and Figure 11 The following results are shown.

[0064] Figure 10 This is a graph representing the pressure loss (dP) and heat transfer coefficient (h) in response to changes in the outer diameter range A based on the cut width B.

[0065] As the cutting width B increases, the pressure loss changes by approximately 20%, and the heat transfer coefficient changes by approximately 10%.

[0066] More specifically, considering the pressure loss, heat transfer coefficient, and durability of the heat dissipation fins 200 and the plate 100, the cutting start point S on the side of the first connector port 130 in the outer diameter range A can start at 22.4 mm, and the cutting end point E on the side of the second connector port 140 can end at 0 mm of the second connector port 140, so that the non-heat dissipation fin portion 210 can be formed within the shortest distance range between the first connector port 130 and the second connector port 140.

[0067] In addition, the non-heat dissipation fin portion 210 may have a width of 1 mm to 1.5 mm in the direction from the edge of the heat dissipation fin 200 to the interior.

[0068] Figure 11 This is a graph representing the pressure loss (dP) and heat transfer coefficient (h) in response to changes in the cut width B based on the outer diameter range A.

[0069] The pressure loss (dP) can be the pressure difference of the fluid passing through the plate 100 between the inlet port 110 and the outlet port 120, and the heat transfer coefficient (h) can be the heat transfer performance coefficient of the heat exchanger including the plate 100.

[0070] When the cut width B is 1.5 mm, the pressure loss increases by 30% or more compared to the case where the cut width B is 0.5 mm, and the heat transfer coefficient decreases by about 5%. The deterioration of the heat transfer coefficient can be reduced when the pressure loss increases by 30% and the flow rate increases. When the cut width B is 2.5 mm, the heat transfer coefficient deteriorates significantly. Therefore, considering the pressure loss, heat transfer coefficient, and durability of the heat sink fins 200 and the plate 100, the cut width B can be between 1.0 mm and 1.5 mm.

[0071] See Figure 6 In the non-heat dissipation fin portion 210, the cutting width B of the central portion C can be greater than the cutting width B of the cutting start point S and the cutting end point E. That is, the cutting width B of the central portion C is greater than the cutting width B of the cutting start point S and the cutting end point E of the non-heat dissipation fin portion 210. This minimizes the degradation of the durability of the joint between the heat dissipation fin 200 and the plate 100 at the cutting start point S and the cutting end point E, and increases the amount of fluid bypassing the heat dissipation fin 200 through the central portion C of the non-heat dissipation fin portion 210, thereby preventing pressure degradation. In this case, the non-heat dissipation fin portion 210 can have a stepped portion, such as... Figure 7 As shown. Although not shown, the non-heat dissipation fin portion 210 may have an arc shape.

[0072] See Figure 7 (a) and Figure 7 (b) The cutting width B at the starting point S and the cutting width B at the ending point E can be different from each other. That is, the non-heat dissipation fin portion 210 can be shaped as non-horizontal or vertically symmetrical by means of factors such as the coupling durability between the non-heat dissipation fin portion 210 and the plate 100, the fluid pressure, the flow velocity distribution, and the shape of the heat dissipation fins 200.

[0073] In this case, such as Figure 7 As shown in (a), in the non-heat-dissipating fin portion 210, the cutting width B can be increased in the direction from the cutting start point S to the cutting end point E. The non-heat-dissipating fin portion 210 can have a shape in which the cutting width B increases in the direction from the cutting start point S to the cutting end point E, thereby reducing the bypass fluid velocity.

[0074] In addition, such as Figure 7 As shown in (b), in the non-heat-dissipating fin portion 210, the cut width B can decrease in the direction from the cut start point S to the cut end point E. The non-heat-dissipating fin portion 210 can have a shape in which the cut width B decreases in the direction from the cut start point S to the cut end point E, thereby increasing the bypass fluid velocity.

[0075] When the non-heat dissipation fin portion 210 has a gradient shape, the cutting start point S can be formed at the point farthest from the cutting end point E within the outer diameter range A, and the cutting end point E can also be formed at the point farthest from the cutting start point S within the outer diameter range.

[0076] In addition, such as Figure 8 As shown in (a), the non-heat dissipation fin portion 210 can have a shape in which the cutting width B is constant between the cutting start point S and the first point P1, and the cutting width B increases in the direction from the first point P1 to the cutting end point E.

[0077] In addition, such as Figure 8 As shown in (b), the non-heat dissipation fin portion 210 can have a shape in which the cutting width B is constant between the cutting start point S and the first point P1, the cutting width B increases from the first point P1, the cutting width B decreases in the direction from the first point P1 to the second point P2, and the cutting width B is constant between the second point P2 and the cutting end point E.

[0078] Reference Figure 9 The heat exchanger can be configured as a water-cooled condenser 1000. The water-cooled condenser 1000 according to the invention can have a heat exchanger core 1100 in which a coolant flows. The heat exchanger may also include a connector 1300 configured to connect the heat exchanger core 1100 and the receiver dryer 1200.

[0079] The heat exchanger core 1100 may include a flow path for the coolant and a flow path for a fluid other than the coolant, i.e., a flow path for the refrigerant. The water-cooled condenser 1000 may also include a condensation zone in which the refrigerant is condensed when it exchanges heat with the coolant. In this case, the receiver dryer 1200 can separate the gas and liquid from the condensed refrigerant.

[0080] Connector 1300 connects the heat exchanger core 1100 and the receiver dryer 1200, allowing fluid to flow between them. The water-cooled condenser 1000 may also include a subcooled region where the refrigerant is subcooled as it exchanges heat with the refrigerant that has passed through the receiver dryer 1200. Connector 1300 connects and secures the heat exchanger core 1100 and the receiver dryer 1200, which form the condensation region and the subcooled region, respectively.

[0081] Furthermore, the heat exchanger core 1100 is fixed to an external device by a support plate 1400, the support plate being connected to make surface contact with one surface of the heat exchanger core. The support plate 1400 includes a plate surface portion 1411 configured to make surface contact with one surface of the heat exchanger core 1100, and a peripheral portion 1412 bent from the edge of the plate surface portion 1411 and configured to surround a portion of the periphery of the heat exchanger core 1100. Additionally, the heat exchanger core 1100 may also include a reinforcing plate 1500 configured to make surface contact with the plate and inserted between the plates connected to the support plate 1400. At least a portion of the reinforcing plate 1500 is arranged to make surface contact with the front surface of the plate.

[0082] In addition, a bracket 1400a directly connected to the heat exchanger core 1100 can be provided on the other side of the heat exchanger core 1100, and the heat exchanger core 1100 can be fixed to an external device.

[0083] This invention is not limited to the embodiments described above, and its scope of application is entirely different. Of course, various modifications and implementations are possible without departing from the subject matter of the invention as claimed in the claims.

[0084] [Explanation of reference numerals and symbols in the attached figures]

[0085] 1000: Water-cooled condenser; 1100: Heat exchanger core.

[0086] 1200: Receiver dryer; 1300: Connector

[0087] 1400a: bracket, 1400: bracket plate

[0088] 1410: Fixed plate portion; 1411: Plate surface portion

[0089] 1412: Peripheral portion; 1420: Connecting plate portion

[0090] 1500: Reinforcement Plate

[0091] 100: Board, 100a: Lower board

[0092] 100b: Top board, 110: Inlet port

[0093] 120: Outlet port, 130: First connector port

[0094] 140: Second connector port; 200: Heat sink fins

[0095] 210: Non-heat dissipation fins; 220: Holes

[0096] A: Outer diameter range, B: Cutting width

[0097] S: Cutting start point, E: Cutting end point

[0098] C: Central part, P1: First point

[0099] P2: Second point

Claims

1. A heat exchanger, the heat exchanger comprising: Each plate has an inlet port for introducing fluid and an outlet port for discharging the fluid therefrom; as well as Heat dissipation fins inserted between a pair of plates. The inlet port and the outlet port are formed on one side of the plate in the width direction and are spaced apart from each other in the longitudinal direction of the plate. The heat dissipation fins include non-heat dissipation fin portions, which are formed on the opposite side based on the width direction of the plate. The heat exchanger core is formed by stacking multiple plates. The plate includes: A first connector port, the first connector port having an upwardly projecting periphery; and The second connector port has an upwardly protruding periphery. The first connector port and the second connector port are formed on the other side based on the width direction of the plate, and are spaced apart from each other in the longitudinal direction of the plate. The non-heat dissipation fin portion is formed within the maximum distance range between the outer diameters of the first connector port and the second connector port, and is positioned at the edge of the heat dissipation fin. The non-heat dissipation fin portion is formed to include the point furthest from both the inlet port and the outlet port, and The cutting start point of the non-heat dissipation fin portion is located at a point corresponding to the outer diameter range of the first connector port, and the outer diameter range is applied based on the outer diameter in a direction parallel to the longitudinal direction of the plate.

2. The heat exchanger of claim 1, wherein, The non-heat-dissipating fin portion is formed by cutting a portion of the heat-dissipating fins.

3. The heat exchanger of claim 1, wherein, The heat dissipation fins have holes formed corresponding to the inlet port, the outlet port, the first connector port, and the second connector port, and the heat dissipation fins are located on the upper surface of the plate.

4. The heat exchanger of claim 1, wherein, The cut endpoint of the non-heat dissipation fin portion is located at a point corresponding to the outer diameter range of the second connector port, and the outer diameter range is applied based on the outer diameter in a direction parallel to the longitudinal direction of the plate.

5. The heat exchanger of claim 1, wherein, The non-heat dissipation fin portion has a width of 1 mm to 1.5 mm in the direction from the edge of the heat dissipation fin to the interior.

6. The heat exchanger of claim 1, wherein, In the non-heat dissipation fin portion, the cutting width of the central portion is greater than the cutting width at the starting point and the cutting width at the ending point.

7. The heat exchanger of claim 1, wherein, In the non-heat dissipation fin section, the cutting width at the starting point and the cutting width at the ending point are different from each other.

8. The heat exchanger according to claim 7, wherein, In the non-heat dissipation fin portion, the cut width increases in the direction from the cut start point to the cut end point.

9. The heat exchanger according to claim 7, wherein, In the non-heat dissipation fin portion, the cut width decreases in the direction from the cut start point to the cut end point.

10. The heat exchanger according to any one of claims 1 to 9, wherein, Coolant flows through the core of the heat exchanger, and The heat exchanger further includes: Receiver dryer; and A connector configured to connect the heat exchanger core and the receiver dryer.

11. A heat exchanger, the heat exchanger comprising: Each plate has an inlet port for introducing fluid and an outlet port for discharging the fluid therefrom; as well as Heat dissipation fins inserted between a pair of plates. The inlet port and the outlet port are formed on one side of the plate in the width direction and are spaced apart from each other in the longitudinal direction of the plate. The heat dissipation fins include non-heat dissipation fin portions, which are formed on the opposite side based on the width direction of the plate. The heat exchanger core is formed by stacking multiple plates. The plate includes: A first connector port, the first connector port having an upwardly projecting periphery; and The second connector port has an upwardly protruding periphery. The first connector port and the second connector port are formed on the other side based on the width direction of the plate, and are spaced apart from each other in the longitudinal direction of the plate. The non-heat dissipation fin portion is formed within the maximum distance range between the outer diameters of the first connector port and the second connector port, and is positioned at the edge of the heat dissipation fin. In the non-heat dissipation fin portion, the cutting width of the central portion is greater than the cutting width at the starting point and the cutting width at the ending point.

12. A heat exchanger, the heat exchanger comprising: Each plate has an inlet port for introducing fluid and an outlet port for discharging the fluid therefrom; as well as Heat dissipation fins inserted between a pair of plates. The inlet port and the outlet port are formed on one side of the plate in the width direction and are spaced apart from each other in the longitudinal direction of the plate. The heat dissipation fins include non-heat dissipation fin portions, which are formed on the opposite side based on the width direction of the plate. The heat exchanger core is formed by stacking multiple plates. The plate includes: A first connector port, the first connector port having an upwardly projecting periphery; and The second connector port has an upwardly protruding periphery. The first connector port and the second connector port are formed on the other side based on the width direction of the plate, and are spaced apart from each other in the longitudinal direction of the plate. The non-heat dissipation fin portion is formed within the maximum distance range between the outer diameters of the first connector port and the second connector port, and is positioned at the edge of the heat dissipation fin. In the non-heat dissipation fin portion, the cutting width at the starting point and the cutting width at the ending point are different from each other.

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