Patent Application
20230417490
The present invention relates to a heat exchanger, and more particularly, to a heat exchanger having a bypass flow path formed to prevent a pressure loss of a fluid flowing in a plate.
In general, a heat exchanger refers to a device designed to allow two or more fluids to exchange heat with one another. The heat exchanger is used to allow different fluids to exchange heat with one another so that the fluids are cooled or heated. Representatively, the heat exchanger is applied to a vehicle cooling/heating system, a refrigerator, an air conditioner, and the like.
In general, a plate-shaped heat exchanger, which is applied to the vehicle cooling/heating system, has a passageway formed between plates each having a predetermined thickness so that a fluid flows through the passageway. The plate-shaped heat exchanger is characterized in that a plurality of plates is disposed at predetermined intervals so that different fluids alternately flow through passageways between the plurality of plates.
With reference to Korean Patent Application Laid-Open No. 10-2020-0011163, as illustrated in
With reference to Korean Patent No. 10-1206858, as illustrated in
That is, the plate-shaped heat exchanger in the related art uses heat dissipation members such as the chevron part or a heat dissipation fin to dissipate heat from the fluid flowing between the plates. In case that the chevron part and the heat dissipation fin are used, heat dissipation performance of the heat exchanger is improved. However, in case that a shape of the chevron part or heat dissipation fin is perpendicular to a flow of the fluid, there sometimes occurs an adverse effect that causes an excessive loss of pressure of the fluid.
Korean Patent Application Laid-Open No. 10-2020-0011163 (published on Feb. 3, 2020)
Korean Patent No. 10-1206858 (registered on Nov. 26, 2012)
The present invention has been made in an effort to solve the above-mentioned problem, and an object of the present invention is to provide a heat exchanger in which a partial region of a heat dissipation fin inserted into stacked plates is cut, which makes it possible to prevent a pressure loss of a fluid flowing in the stacked plates.
A heat exchanger according to the present invention may include: plates each having an inlet port into which a fluid is introduced, and an outlet port from which the fluid is discharged; and a heat dissipation fin inserted between a pair of plates, in which the inlet port and the outlet port are formed at one side based on a width direction of a plate and spaced apart from each other in a longitudinal direction of the plate, in which the heat dissipation fin includes a non-heat dissipation fin portion formed at the other side based on the width direction of the plate, and in which a heat exchanger core is formed by stacking a plurality of plates.
Further, the non-heat dissipation fin portion may be formed by cutting a part of the heat dissipation fin.
Further, the plate may include: a first junction port having a periphery protruding upward; and a second junction port having a periphery protruding upward, and the first junction port and the second junction port may be formed at the other side based on the width direction of the plate and spaced apart from each other in the longitudinal direction of the plate.
In this case, the heat dissipation fin may have holes formed to correspond to the inlet port, the outlet port, the first junction port, and the second junction port and be seated on an upper surface of the plate.
Further, the non-heat dissipation fin portion may be formed within a maximum distance range between an outer diameter of the first junction port and an outer diameter of the second junction port and positioned at an edge of the heat dissipation fin.
Further, the non-heat dissipation fin portion may be formed to include a point farthest in distance from both the inlet port and the outlet port.
Further, a cut start point of the non-heat dissipation fin portion may be positioned at a point corresponding to an outer diameter range of the first junction port, and an outer diameter based on a direction parallel to a direction from one side to the other of the plate may be applied to the outer diameter range.
Further, a cut end point of the non-heat dissipation fin portion may be positioned at a point corresponding to an outer diameter range of the second junction port, and the outer diameter based on a direction parallel to the direction from one side to the other of the plate may be applied to the outer diameter range.
Further, the non-heat dissipation fin portion may have a width of 1 to 1.5 mm in a direction from an edge to the inside of the heat dissipation fin.
Further, in the non-heat dissipation fin portion, a cut width of a central portion may be larger than a cut width of a cut start point and a cut width of a cut end point.
Further, in the non-heat dissipation fin portion, a cut width of a cut start point and a cut width of a cut end point may be different from each other.
In this case, in the non-heat dissipation fin portion, the cut width may increase in a direction from the cut start point to the cut end point.
In addition, in the non-heat dissipation fin portion, the cut width may decrease in a direction from the cut start point to the cut end point.
A water-cooled condenser according to the present invention includes the heat exchanger, in which 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.
With the above-mentioned configuration, the heat exchanger according to the present invention may maintain maximum performance in dissipating heat from the fluid flowing through the space defined by stacking the pair of plates and minimize a pressure loss caused by an increase in flow path of the fluid due to the shape of the heat dissipation fin.
Hereinafter, the technical spirit of the present invention will be described in more detail using the accompanying drawings. In addition, terms or words used in the specification and the claims should not be interpreted as being limited to a general or dictionary meaning and should be interpreted as a meaning and a concept which conform to the technical spirit of the present invention based on a principle that an inventor can appropriately define a concept of a term in order to describe his/her own invention by the best method. Therefore, the exemplary embodiments disclosed in the present specification and the configurations illustrated in the drawings are just the best preferred exemplary embodiments of the present invention and do not represent all the technical spirit of the present invention. Accordingly, it should be appreciated that various modified examples capable of substituting the exemplary embodiments may be made at the time of filing the present application.
Hereinafter, the technical spirit of the present invention will be described in more detail using the accompanying drawings. The accompanying drawings are only exemplary embodiments illustrated to explain the technical spirit of the present invention in more detail, and the technical spirit of the present invention is not limited to the form of the accompanying drawings.
With reference to
The fluid, which flows through a space defined by stacking the pair of plates 100a and 100b, may be oil or a coolant. However, the type of fluid is not limited. The fluid may be introduced into the inlet port 110, flow through the space between the pair of plates 100a and 100b, and be discharged to the outlet port 120. A partition wall is formed around the plate 100 to prevent the fluid from leaking to the outside of the plate 100.
The heat dissipation fin 200 has a shape in which structures horizontal with respect to a flow direction of the fluid and structures perpendicular to the flow direction of the fluid are repeatedly coupled, thereby improving an effect of dissipating heat from the fluid flowing through the space between the pair of plates 100a and 100b.
The non-heat dissipation fin portion 210 may be formed by cutting a part of the heat dissipation fin 200 and provided at the other side based on the width direction of the plate 100.
In addition, the plate 100 may include a first junction port 130 having a periphery protruding upward, and a second junction port 140 having a periphery protruding upward. The first junction port 130 and the second junction port 140 may be formed at the other side based on the width direction of the plate 100 and spaced apart from each other in the longitudinal direction of the plate 100.
As illustrated in
In case that the pair of plates 100a and 100b is stacked, the peripheries of the first and second junction ports 130 and 140 protrude and thus are physically separated from the space between the inlet port 110, the outlet port 120, and the pair of plates 100a and 100b. The heat dissipation fin 200 is inserted into the space between the pair of plates 100a and 100b, such that a position of the heat dissipation fin 200 is fixed.
Furthermore, the heat dissipation fin 200 may have holes 220 formed to correspond to the inlet port 110, the outlet port 120, the first junction port 130, and the second junction port 140 and be seated on an upper surface of the plate 100. That is, the heat dissipation fin 200 may be seated on the upper surface of the plate 100 and have the holes 220 corresponding in sizes and positions to the inlet port 110, the outlet port 120, the first junction port 130, and the second junction port 140 formed in the plates 100. Therefore, it is possible to minimize hindrance to the flow of the fluid, improve overall performance in dissipating heat from the fluid, and prevent a deterioration in coupling force between the pair of plates 100a and 100b.
A flow distance of the fluid is increased by the shape of the heat dissipation fin 200 having the structure perpendicular to the flow direction, which may cause a pressure loss. Therefore, to minimize the pressure loss, the heat dissipation fin 200 according to the present invention includes the non-heat dissipation fin portion 210 so that the fluid may bypass the heat dissipation fin 200 and move toward the outlet port 120 without receiving resistance.
In this case, the non-heat dissipation fin portion 210 is formed by cutting a part of the heat dissipation fin 200. The non-heat dissipation fin portion 210 refers to a space formed by machining (cutting) a part of the heat dissipation fin 200 or bending a part of the heat dissipation fin 200 in a direction perpendicular to a direction of a surface of the heat dissipation fin 200 so that the heat dissipation fin 200 is not formed.
Therefore, the heat exchanger according to the present invention may maintain maximum performance in dissipating heat from the fluid flowing through the space defined by stacking the pair of plates 100a and 100b and minimize a pressure loss caused by an increase in flow path of the fluid due to the shape of the heat dissipation fin 200.
With reference to
In addition, the non-heat dissipation fin portion 210 may be formed within a maximum distance range between an outer diameter of the first junction port 130 and an outer diameter of the second junction port 140 and provided at an edge of the heat dissipation fin 200. That is, two opposite ends (a cut start point and a cut end point) of the non-heat dissipation fin portion 210 may be positioned within the maximum distance range between the outer diameter of the first junction port 130 and the outer diameter of the second junction port 140 and provided at an edge, i.e., a rim of the heat dissipation fin 200. The edge of the heat dissipation fin 200 is a region in which the hindrance to the flow of the fluid caused by the heat dissipation fin 200 is lowest, and a flow velocity of the fluid 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 the fluid, which is hindered by the heat dissipation fin 200, may bypass the heat dissipation fin 200, such that the flow velocity of the fluid, which bypasses the heat dissipation fin 200, may be maximized, thereby minimizing a pressure loss.
In this case, the non-heat dissipation fin portion 210 may include a point farthest in distance from both the inlet port 110 and the outlet port 120. That is, the non-heat dissipation fin portion 210 may include a point, on the heat dissipation fin 200, farthest in distance from the inlet port 110 and the outlet port 120, i.e., a point between a protruding portion of the first junction port 130 and a protruding portion of the second junction port 140. Therefore, the non-heat dissipation fin portion 210 may be positioned in a region, in which a highest degree of hindrance is applied to the flow of the fluid, and allow the fluid to bypass the heat dissipation fin 200, thereby effectively preventing a pressure loss.
With reference to
In addition, in the non-heat dissipation fin portion 210, a cut end point E may be positioned at a point corresponding to the outer diameter range A of the second junction port 140, and the outer diameter based on the direction parallel to the direction from one side to the other of the plate 100 may be applied to the outer diameter range A.
In case that an outer diameter of each of the first and second junction ports 130 and 140 is 22.4 mm, the performance analysis related to the start point S, the end point E, and a cut width B of the non-heat dissipation fin portion 210 will be described below.
As shown in Table 1, in case that the cut width B of 0.5 mm to 2.5 mm is applied when the outer diameter range A is 0 mm to 22.4 mm,
the following results illustrated in
[
When the cut width B increases, a pressure loss varies by about 20%, and a heat transfer coefficient varies by about 10%.
Most particularly, in consideration of the pressure loss, the heat transfer coefficient, and durability of the heat dissipation fin 200 and the plate 100, the cut start point S at the side of the first junction port 130 in the outer diameter range A may start at 22.4 mm, and the cut end point E at the side of the second junction port 140 may end at 0 mm of the second junction port 140, such that the non-heat dissipation fin portion 210 may be formed within a shortest distance range between the first junction port 130 and the second junction port 140.
Furthermore, the non-heat dissipation fin portion 210 may have a width of 1 to 1.5 mm in a direction from the edge to the inside of the heat dissipation fin 200.
[
The pressure loss (dP) may be a difference in pressure of the fluid passing through the plate 100 between the inlet port 110 and the outlet port 120, and the heat transfer coefficient (h) may be a heat transfer performance coefficient of the heat exchanger including the plate 100.
When the cut width B is 1.5 mm, the pressure loss is improved by 30% or more, and the heat transfer coefficient is degraded by about 5%, in comparison with the case in which the cut width B is 0.5 mm. The deterioration in heat transfer coefficient may be reduced as the pressure loss is improved by 30% and a flow rate is increased. The heat transfer coefficient greatly deteriorates when the cut width B is 2.5 mm. Therefore, the cut width B may be at a level of 1.0 to 1.5 mm in consideration of the pressure loss, the heat transfer coefficient, and the durability of the heat dissipation fin 200 and the plate 100.
With reference to
With reference to
In this case, as illustrated in
n addition, as illustrated in
When the non-heat dissipation fin portion 210 has a shape having a gradient, the cut start point S may be formed at a point farthest from the cut end point E within the outer diameter range A, and the cut end point E may also be formed at a point farthest from the cut start point S within the outer diameter range.
In addition, as illustrated in
In addition, as illustrated in
With reference to
The heat exchanger core 1100 may include a flow path through which the coolant flows, and a flow path through which a fluid, which is different from the coolant, flows, i.e., a flow path through which a refrigerant flows. The water-cooled condenser 1000 may further include a condensing region in which the refrigerant is condensed as the refrigerant and the coolant exchange heat with each other. In this case, the receiver dryer 1200 may separate gas and liquid from the condensed refrigerant.
The connector 1300 may connect the heat exchanger core and the receiver dryer so that the fluid flows between the heat exchanger core 1100 and the receiver dryer 1200. The water-cooled condenser 1000 may further include a supercooling region in which the refrigerant is supercooled as the coolant and the refrigerant having passed through the receiver dryer 1200 exchange heat with each other. The connector 1300 connects and fixes the heat exchanger core 1100 and the receiver dryer 1200 that form the condensing region and the supercooling region.
In addition, the heat exchanger core 1100 is fixed to an external device by a bracket plate 1400 connected to be in surface contact with one surface of the heat exchanger core 1100. The bracket plate 1400 includes a plate surface portion 1411 provided to be in surface contact with one surface of the heat exchanger core 1100, and a peripheral portion 1412 bent from an edge of the plate surface portion 1411 and provided to surround a part of a periphery of the heat exchanger core 1100. In addition, the heat exchanger core 1100 may further include a reinforcement plate 1500 disposed to be in surface contact with the plates and interposed between the plates connected to the bracket plate 1400. At least a part of the reinforcement plate 1500 is disposed to be in surface contact with a front surface of the plate.
In addition, a bracket 1400a, which is connected directly to the heat exchanger core 1100, may be provided at the other side of the heat exchanger core 1100 and fix the heat exchanger core 1100 to the external device.
The present invention is not limited to the above embodiments, and the scope of application is diverse. Of course, various modifications and implementations are possible without departing from the subject matter of the present invention claimed in the claims.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10-2021-0023343 | Feb 2021 | KR | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/KR2022/002129 | 2/14/2022 | WO |
