WO2016032255A1 - 증발기 - Google Patents
증발기 Download PDFInfo
- Publication number
- WO2016032255A1 WO2016032255A1 PCT/KR2015/008989 KR2015008989W WO2016032255A1 WO 2016032255 A1 WO2016032255 A1 WO 2016032255A1 KR 2015008989 W KR2015008989 W KR 2015008989W WO 2016032255 A1 WO2016032255 A1 WO 2016032255A1
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- WO
- WIPO (PCT)
- Prior art keywords
- header tank
- region
- evaporator
- tubes
- row
- Prior art date
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
- F28F1/26—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means being integral with the element
- F28F1/28—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means being integral with the element the element being built-up from finned sections
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
Definitions
- the present invention relates to an evaporator, and in more detail, has an eight-pass flow in the first to eighth regions, and thus the refrigerant is evenly distributed in each region, thereby reducing the temperature variation and increasing the heat exchange efficiency with the outside air.
- the present invention relates to an evaporator capable of maintaining comfort of passengers by having an even temperature distribution of air discharged to the left and right of a car interior.
- the evaporator is a component of the air conditioner which cools the air introduced by the blower in the process of changing the liquid heat exchange medium into a gas state by cooling the heat by the heat exchange.
- FIG. 1 A conventional evaporator is shown in FIG. 1, and FIGS. 2 to 4 show a schematic diagram of an internal refrigerant flow of FIG. 1, a temperature analysis result of a second row, and a refrigerant velocity analysis result.
- the conventional evaporator 80 shown in FIGS. 1 and 2 is partitioned inside the first and second rows by the partition wall 70 and is spaced apart by a predetermined distance from the first header tank 10 and the second row.
- the refrigerant introduced into the first row through the inlet pipe 30 is moved to the second header tank 20 through the tube 61 while moving in the longitudinal direction inside the first header tank 10.
- a second region A2 (lower-> up) which is moved back to the first header tank 10 through another tube 61;
- a third area A3 which is moved back to the second header tank 20 through the other tube 61;
- the fourth area A4 (below) moved to the first header tank 10 (below -> Phase);
- a fifth region A5 up-> down
- the outlet pipe 40 is discharged.
- the evaporator as described above concentrates refrigerant in an area adjacent to the inlet pipe and the outlet pipe, and in particular, the second row provided with the outlet pipe is prevented from pulling due to refrigerant inertia.
- a region in which the refrigerant flow is weak exists, and the temperature rises in this region.
- a section over a predetermined speed is indicated by hatching. More specifically, the evaporator as described above exists in a region of 8 to 10 ° C relatively high temperature, the temperature difference between the fourth region and the sixth region is generated up to 8 ° C.
- the object of the present invention is to have an eight-pass flow of the first to eighth zone (Pass) flow is evenly distributed in each area to reduce the temperature variation
- the object of the present invention is to have an eight-pass flow of the first to eighth zone (Pass) flow is evenly distributed in each area to reduce the temperature variation
- the evaporator of the present invention is divided into a first row and a second row by the partition wall, the first header tank and the second header tank which are provided side by side spaced apart at a predetermined distance;
- a baffle provided inside the first header tank and the second header tank to control the flow of the refrigerant;
- a core portion including a plurality of tubes fixed at both ends in first and second rows of the first header tank and the second header tank, and a pin interposed between the tubes, wherein the tube includes the first header. At least four regions each of which is moved from the tank to the second header tank or from the second header tank to the first header tank are formed in each of the first row and the second row.
- the evaporator includes an inlet pipe communicating with the first row and an outlet pipe communicating with the second row side by side on one side of the first header tank, wherein the tube is connected to the inlet pipe in the first row.
- a first region in which the refrigerant flowed through is moved from the first header tank to the second header tank, a second region is moved from the second header tank to the first header tank, and the first header tank to the second header tank.
- the eighth area sequentially And it is characterized in that which is discharged through the outlet pipe. That is, the evaporator of the present invention has an eight-pass flow of the first to eighth regions, and the temperature variation can be reduced by evenly distributing the refrigerant in each region. Accordingly, the evaporator of the present invention can increase the heat exchange efficiency with the outside air, there is an advantage that the air discharged to the left and right of the interior of the vehicle has an even temperature distribution can maintain the passenger comfort.
- the tube has the same flow path area of each of the plurality of tubes, the total circumferential length of each of the plurality of tubes is the same, the hydraulic diameter is 1.0 to 2.8 mm, the evaporator 150 to 300 width of the core portion In mm, through this, the evaporator of the present invention has the advantage of improving the heat dissipation performance while reducing the temperature deviation.
- the evaporator has the same number of tubes forming the first and eighth regions, the same number of tubes forming the second and seventh regions, and the third and sixth regions. Since the number of tubes to be formed is the same and the number of tubes forming the fourth and fifth regions is the same, the baffles are provided at the same position so that they can be formed symmetrically with each other in the width direction. have.
- the first header tank and the second header tank have the same number of baffles positioned in the first row and the second row, respectively, and the positions of the baffles positioned in the first row and the second row in the longitudinal direction are the same. It is possible to further increase the manufacturability.
- the evaporator has the same number of tubes forming a region facing each other in the first row and the second row, but the number of tubes in the eighth region is less than or equal to the number of tubes in the seventh region,
- the number of tubes may be less than or equal to the number of tubes in the sixth region, and the number of tubes in the sixth region may be less than or equal to the number of tubes in the fifth region.
- the evaporator of the present invention can prevent the refrigerant from flowing in the region adjacent to the outlet side by forming the same number of tubes forming the region near the outlet side or less than the adjacent region.
- the evaporator of the present invention has an eight-pass flow of the first to eighth regions to distribute the refrigerant evenly to each region, thereby reducing the temperature variation and increasing the heat exchange efficiency with the outside air, Air discharged to the left and right of the vehicle has an even temperature distribution has the advantage of maintaining the comfort of the passengers.
- FIG. 1 and 2 are a perspective view and a refrigerant flow schematic showing a conventional evaporator.
- FIGS. 1 and 2 are second column side temperature analysis graph of the evaporator illustrated in FIGS. 1 and 2.
- FIG. 5 is a perspective view showing an evaporator of the present invention.
- 6 and 7 are refrigerant flow charts of the evaporator shown in FIG.
- FIG. 8 is a front view of the evaporator shown in FIG.
- FIG. 9 is a detailed view of the tube and fin of the evaporator shown in FIG.
- FIG. 10 is another perspective view showing an evaporator of the present invention.
- 11 is a second column-side temperature analysis graph of the evaporator according to the present invention.
- FIG. 12 is a graph illustrating a refrigerant velocity analysis of an evaporator according to the present invention.
- Fig. 13 is a graph showing the relationship between the tube hydraulic diameter, the maximum temperature difference, and the heat dissipation performance.
- first header tank 200 second header tank
- A1 first area
- A2 second area
- A3 third area
- A4 fourth area
- A5 Fifth Area
- A6 Sixth Area
- A7 seventh area
- A8 second area
- FIG. 5 is a perspective view showing an evaporator 1000 of the present invention
- Figures 6 and 7 is a flow chart of the refrigerant of the evaporator 1000 shown in FIG. 5
- Figure 8 is a view of the evaporator 1000 shown in FIG. 9 is a detailed view of the tube 510 and the fin 520 of the evaporator 1000 shown in FIG. 5
- FIG. 10 is another perspective view showing the evaporator 1000 of the present invention
- Figure 12 is a refrigerant velocity analysis graph of the evaporator 1000 according to the present invention
- Figure 13 is a tube 510 hydraulic diameter, the maximum temperature difference and heat dissipation It is a relationship graph of performance
- FIG. 14 is a relationship graph of the width of a core part and heat dissipation performance.
- the evaporator 1000 of the present invention includes a first header tank 100, a second header tank 200, a baffle 600, and a core part 500.
- the first header tank 100 and the second header tank 200 are configured to be spaced apart from each other at a predetermined distance and are arranged side by side.
- Each of the first header tank 100 and the second header tank 200 is partitioned into a first row and a second row by partition walls, and an inlet pipe through which refrigerant is introduced. 300 and the outlet pipe 400 is connected.
- the inlet pipe 300 is connected to the first row to introduce a refrigerant
- the outlet pipe 400 is connected to the second column to discharge the refrigerant.
- the inlet pipe 300 and the outlet pipe 400 may be connected to one side of the first header tank 100 side by side in the form of a pipe (see FIG. 10), or may be in the form of a “C” shaped manifold (see FIG.
- the inlet pipe 300 and the outlet pipe 400 is a "C" shaped manifold form
- the inlet pipe 300 is in communication with the first row is bent in the width direction again from the downward direction
- the outlet pipe 400 communicates with the second row and extends in the width direction.
- the "C" shaped manifold shape when the evaporator 1000 is viewed from one side of the first header tank 100, the overall shape is "C" shaped, the inlet pipe 300 and the outlet pipe
- the manifold structure for forming the 400 is a first member (not shown) directly coupled to the first header tank 100, and a first member coupled to the first member to form a refrigerant flow space therein. It may include two members (not shown).
- 5 to 8 illustrate an example in which the inlet pipe 300 and the outlet pipe 400 extend in the width direction toward the side where the second row, which is the front side of the drawing, is located.
- the first header tank 100 and the second header tank 200 are spaced apart in the height direction, and the first header tank 100 is positioned at an upper side and at a rear side thereof.
- the first row is formed
- the second row is formed on the front side
- the inlet pipe 300 and the outlet pipe 400 are shown on the left side of the drawing, but the evaporator 1000 of the present invention is not limited thereto.
- the first header tank 100 and the second header tank 200 may be located opposite to the upper and lower sides, or may be spaced apart in the vertebral direction, and the positions of the first row and the second row may also be changed.
- the baffle 600 is provided in the first header tank 100 and the second header tank 200 to control the flow of the refrigerant, and the first header tank 100 and the second header tank 200 are provided. It is formed in a plate shape to block the flow of the refrigerant in the longitudinal direction of the), and adjusts the position of the baffle 600 to adjust the number of tubes 510 forming the first region (A1) to eighth region (A8). Can be.
- the core part 500 may include a tube 510 and a fin 520, and side plates 530 supporting the tube 510 and the fin 520 may be further provided at both ends.
- Both ends of the tube 510 are fixed to the first row and the second row of the first header tank 100 and the second header tank 200 to form a coolant flow path, and the fin 520 is the It is interposed between the tubes 510.
- the plurality of tubes 510 are provided, and the plurality of tubes 510 are all in the same shape, and more specifically, each flow path area and the total circumferential length of the flow path are the same.
- the tube 510 is moved from the first header tank 100 to the second header tank 200 in the first row and the second row, or the first header tank 100 in the second header tank 200. It is preferable that each of the regions to be moved by) is provided with four or more in the longitudinal direction.
- the tube 510 forms the first region A1 to the fourth region A4 through which the refrigerant introduced through the inlet pipe 300 is transferred in the first row, and the fifth region in the second row. (A5) to eighth region A8 are formed.
- the first area A1 to the fourth area A4 are areas formed by the tube 510 in the first row and sequentially along the length direction of the first header tank 100. Is formed.
- the first region A1 is a first region in which the refrigerant introduced through the inlet pipe 300 is moved, and the refrigerant is introduced through the inlet pipe 300 to the region blocked by the baffle 600.
- the second region A2 is a region in which the refrigerant passing through the first region A1 is moved, and is formed adjacent to the first region A1 in the longitudinal direction of the first header tank 100. The refrigerant in the second header tank 200 is moved to the first header tank 100.
- the third region A3 is a region in which the refrigerant passing through the second region A2 is moved, and is formed adjacent to the second region A2 in the longitudinal direction of the first header tank 100.
- the refrigerant in the first header tank 100 is moved to the second header tank 200.
- the fourth region A4 is a region in which the refrigerant passing through the third region A3 is moved, and is formed adjacent to the third region A3 in the longitudinal direction of the first header tank 100.
- the refrigerant in the second header tank 200 is moved to the first header tank 100.
- the fifth region A5 to the sixth region A6 are regions formed by the tube 510 in the second row, and the refrigerant passing through the fourth region A4 moves to the second row.
- the refrigerant in the first header tank 100 is moved to the second header tank 200.
- the sixth region A6 is a region in which the refrigerant passing through the fifth region A5 is moved, and is formed adjacent to the fifth region A5 in the longitudinal direction of the first header tank 100.
- the refrigerant in the second header tank 200 is moved to the first header tank 100.
- the seventh region A7 is a region in which the refrigerant passing through the sixth region A6 is moved, and is formed adjacent to the sixth region A6 in the longitudinal direction of the first header tank 100.
- the refrigerant in the first header tank 100 is moved to the second header tank 200.
- the eighth region A8 is a region in which the refrigerant passing through the seventh region A7 is moved, and is formed adjacent to the seventh region A7 in the longitudinal direction of the first header tank 100.
- the refrigerant in the second header tank 200 is moved to the first header tank 100.
- the eighth region A8 is a portion in communication with the outlet pipe 400, and the refrigerant flowing through the inlet pipe 300 sequentially flows through the first region A1 to the eighth region A8. It is discharged through the outlet pipe 400.
- the evaporator 1000 of the present invention has an eight-pass flow of the first region A1 to the eighth region A8, and the temperature variation may be reduced by evenly distributing the refrigerant in each region. Accordingly, the evaporator 1000 of the present invention can increase the heat exchange efficiency with the outside air, and has the advantage that the air discharged to the left and right of the vehicle interior has an even temperature distribution to maintain the comfort of the passengers.
- the number of tubes 510 of the eighth region A8 is less than or equal to the number of tubes 510 of the seventh region A7
- the number of tubes 510 is less than or equal to the number of tubes 510 of the sixth region A6
- the number of tubes 510 of the sixth region A6 is the tube 510 of the fifth region A5. ) May be less than or equal to the number.
- the number of tubes 510 of the eighth region A8 and the seventh region A7 is four, and the number of tubes 510 of the sixth region A6 and the fifth region A5 is five.
- An individual example is shown.
- the evaporator 1000 of the present invention is not limited thereto, and Table 1 below shows the number of tubes 510 forming each possible region in the evaporator 1000 of the present invention.
- the total number of tubes 510 refers to the number of rows of tubes positioned in the longitudinal direction of the first header tank 100.
- limiting the number of tubes 510 forming the fifth region (A5) to the eighth region (A8) forming the second row is the second row air in the air flow direction The area where the first encounters the?, After passing through the second row, the temperature deviation in the second row is greater than the temperature deviation in the first row as it passes through the first row. Accordingly, in the case of the evaporator 1000, it is important to eliminate the refrigerant deflection in the second row in reducing the variation in the air temperature as a whole by cooling the air primarily cooled in the second row again in the first row.
- the evaporator 1000 of the present invention may prevent the refrigerant from flowing in the region adjacent to the outlet side because the number of tubes 510 forming the region near the outlet side is the same or less than that of the adjacent region.
- the number of tubes 510 may not be a multiple of four
- the number of tubes 510 of the eighth region A8 closest to the outlet side is the number of tubes 510 of the seventh region A7.
- the number of tubes 510 of the seventh region A7 is less than or equal to the number of tubes 510 of the sixth region A6, and
- the number of tubes 510 of the sixth region A6 may be less than or equal to the number of tubes 510 of the fifth region A5.
- the number of tubes 510 may be equal to each other to form a region facing each other in the first row and the second row.
- the tube 510 has the same number of tubes 510 forming the first area A1 and the eighth area A8, and the second area A2 and the seventh area A7. ),
- the number of tubes 510 forming the same number is the same
- the number of tubes 510 forming the third region A3 and the sixth region A6 is the same
- the fourth region A4 and the fourth It is preferable that the number of tubes 510 forming five regions A5 is the same.
- the baffle 600 for controlling the refrigerant flow in the first header tank 100 and the second header tank 200 is the baffle 600 is the first header tank 100.
- the number of columns provided in the first row and the second row in the second header tank 200 are the same, and the positions provided in the first row and the second row in the lengthwise direction are the same, so that the manufacturing is easy. .
- the evaporator 1000 of the present invention preferably has a hydraulic diameter of 1.0 to 2.8 mm of the tube 510.
- the hydraulic diameter refers to the flow path area St of the 4 X tube 510 / the length around the entire flow path of the tube 510.
- FIG. 9 (a) and 9 (b) show cross sections of the tube 510, which is the sum of the areas of the respective portions of the refrigerant flowing on the cross section of the tube 510 in FIG. 9 (a).
- the flow path area St of the tube 510 is indicated by hatching, and the entire circumferential length Lt and the circumferential length of each portion of the refrigerant flows on the cross section of the tube 510 in FIG. 9B. As shown.
- FIG. 11 is a second column-side temperature analysis graph of the evaporator 1000 according to the present invention
- Figure 12 is a refrigerant velocity analysis graph of the evaporator 1000 according to the present invention.
- the evaporator 1000 according to the present invention does not have a temperature section of 8 to 10 ° C. itself, as compared to the temperature analysis graph of the evaporator shown in FIG. 3, and 6 to 8 ° C. It can be seen that the area of is also small.
- FIG. 12 is indicated by hatching an area of a predetermined speed or more.
- the evaporator 1000 according to the present invention is compared with the refrigerant velocity analysis graph of the evaporator shown in FIG. 4.
- the evaporator 1000 of the present invention can reduce the pulling due to the coolant inertia and the temperature deviation caused by the refrigerant inertia adjacent to the region where the inlet pipe 300 and the outlet pipe 400 are provided.
- the temperature difference can be reduced, and the overall heat dissipation performance can be further increased.
- the hydraulic diameter of the tube 510 when the hydraulic diameter of the tube 510 is less than 1.0 mm, the heat dissipation performance is sharply lowered.
- the tube diameter is larger than 2.8 mm, the maximum temperature difference is increased, so that the maximum temperature difference is reduced, and the heat dissipation is reduced.
- the hydraulic diameter of the tube 510 of the evaporator 1000 of the present invention is preferably 1.0 to 2.8 mm so as to sufficiently secure the performance.
- the evaporator 1000 of the present invention preferably has a width Wcore of 150 to 300 mm.
- 14 is a graph showing the relationship between the width Wcore of the core of the tube 510 having a hydraulic diameter of 1.0 mm and a diameter of 2.8 mm, and the heat dissipation performance.
- the width Wcore of the core is less than 150 mm or 300 mm. It can be seen that the heat dissipation performance is sharply reduced when it exceeds.
- the evaporator 1000 of the present invention has a hydraulic diameter of 1 to 2.8 mm of the tube 510 and a width Wcore of 150 to 300 mm to reduce the temperature deviation while providing heat dissipation performance. There is an advantage to improve.
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Abstract
Description
튜브(510)의 총 개수 | 제1영역(A1)(제8영역(A8)) | 제2영역(A2)(제7영역(A7)) | 제3영역(A3)(제6영역(A6)) | 제4영역(A4)(제5영역(A5)) |
4N | N | N | N | N |
4N+1 | N | N | N | N+1 |
4N+2 | N | N | N+1 | N+1 |
4N+3 | N | N+1 | N+1 | N+1 |
Claims (14)
- 내부가 격벽에 의해 제1열 및 제2열로 구획되며, 일정거리 이격되어 나란하게 구비되는 제1헤더탱크(100) 및 제2헤더탱크(200);상기 제1헤더탱크(100) 및 제2헤더탱크(200) 내부에 구비되어 냉매의 유동을 조절하는 배플(600);상기 제1헤더탱크(100) 및 제2헤더탱크(200)의 제1열 및 제2열에 각각 양단이 고정되는 복수개의 튜브(510)와, 상기 튜브(510) 사이에 개재되는 핀(520)을 포함하는 코어부(500)를 포함하며,상기 튜브(510)는 상기 제1헤더탱크(100)에서 제2헤더탱크(200)로 이동되거나 제2헤더탱크(200)에서 제1헤더탱크(100)로 이동되는 영역이 제1열 및 제2열 각각 4개 이상 형성되는 것을 특징으로 하는 증발기.
- 제1항에 있어서,상기 증발기(1000)는 상기 제1헤더탱크(100)의 일측에 나란하게 상기 제1열과 연통되는 입구파이프(300) 및 상기 제2열과 연통되는 출구파이프(400)를 포함하는 것을 특징으로 하는 증발기.
- 제1항에 있어서,상기 증발기(1000)는 상기 제1헤더탱크(100)의 일측에 “C”자형 매니폴드 형태로, 상기 제1열과 연통되어 하측방향에서 다시 폭방향으로 절곡되어 연장되는 입구파이프(300) 및 상기 제2열과 연통되어 폭방향으로 연장되는 출구파이프(400)를 포함하는 것을 특징으로 하는 증발기.
- 제2항 또는 제3항에 있어서,상기 튜브(510)는 상기 제1열에서, 상기 입구파이프(300)를 통해 유입된 냉매가 상기 제1헤더탱크(100)로부터 제2헤더탱크(200)로 이동되는 제1영역(A1), 상기 제2헤더탱크(200)로부터 제1헤더탱크(100)로 이동되는 제2영역(A2), 상기 제1헤더탱크(100)로부터 제2헤더탱크(200)로 이동되는 제3영역(A3), 및 상기 제2헤더탱크(200)로부터 제1헤더탱크(100)로 이동되는 제4영역(A4)을 순차적으로 통과하여 상기 제2열로 이동되고, 상기 제1헤더탱크(100)로부터 제2헤더탱크(200)로 이동되는 제5영역(A5), 상기 제2헤더탱크(200)로부터 제1헤더탱크(100)로 이동되는 제6영역(A6), 상기 제1헤더탱크(100)로부터 제2헤더탱크(200)로 이동되는 제7영역(A7), 및 상기 제2헤더탱크(200)로부터 제1헤더탱크(100)로 이동되는 제8영역(A8) 순차적으로 통과하여 상기 출구파이프(400)를 통해 배출되는 것을 특징으로 하는 증발기.
- 제4항에 있어서,상기 증발기(1000)는 복수개의 상기 튜브(510) 각각의 유로면적(St)이 동일하고, 복수개의 상기 튜브(510) 각각의 유로 전체 둘레 길이(Lt)가 동일한 것을 특징으로 하는 증발기.
- 제5항에 있어서,상기 튜브(510)는 아래 수학식 1에 의해 정의되는 수력직경이 1.0 내지 2.8 mm인 것을 특징으로 하는 증발기.[수학식 1]수력직경 = 4 X 튜브(510)의 유로면적(St) / 튜브(510) 유로의 전체 둘레 길이(Lt)
- 제6항에 있어서,상기 증발기(1000)는 상기 코어부(500)의 너비(Wcore)가 150 내지 300 mm인 것을 특징으로 하는 증발기.
- 제5항에 있어서,상기 증발기(1000)는 상기 제8영역(A8)의 튜브(510) 개수가 상기 제7영역(A7)의 튜브(510) 개수보다 적거나 같은 것을 특징으로 하는 증발기.
- 제5항에 있어서,상기 증발기(1000)는 상기 제7영역(A7)의 튜브(510) 개수가 상기 제6영역(A6)의 튜브(510) 개수보다 적거나 같은 것을 특징으로 하는 증발기.
- 제5항에 있어서,상기 제6영역(A6)의 튜브(510) 개수가 상기 제5영역(A5)의 튜브(510) 개수보다 적거나 같은 것을 특징으로 하는 증발기.
- 제5항에 있어서,상기 제1헤더탱크(100) 및 제2헤더탱크(200)는 각각 상기 제1열 및 제2열에 위치되는 배플(600)의 개수가 동일한 것을 특징으로 하는 증발기.
- 제11항에 있어서,상기 제1헤더탱크(100) 및 제2헤더탱크(200)는 각각 길이방향으로 상기 제1열 및 제2열에 위치되는 배플(600)의 위치가 동일한 것을 특징으로 하는 증발기.
- 제12항에 있어서,상기 증발기(1000)는 제1열과 제2열의 마주하는 영역을 형성하는 튜브(510)의 개수가 동일한 것을 특징으로 하는 증발기.
- 제13항에 있어서,상기 제1영역(A1) 및 제8영역(A8)을 형성하는 튜브(510)의 개수가 동일하고, 상기 제2영역(A2) 및 제7영역(A7)을 형성하는 튜브(510)의 개수가 동일하며, 상기 제3영역(A3) 및 제6영역(A6)을 형성하는 튜브(510)의 개수가 동일하고, 상기 제4영역(A4) 및 제5영역(A5)을 형성하는 튜브(510)의 개수가 동일한 것을 특징으로 하는 증발기.
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DE112015000146.8T DE112015000146T5 (de) | 2014-08-29 | 2015-08-27 | Verdampfer |
US14/916,237 US9919584B2 (en) | 2014-08-29 | 2015-08-27 | Evaporator |
CN201580001921.2A CN105593617B (zh) | 2014-08-29 | 2015-08-27 | 蒸发器 |
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KR20140114298 | 2014-08-29 | ||
KR10-2014-0114298 | 2014-08-29 | ||
KR1020150120913A KR102224130B1 (ko) | 2014-08-29 | 2015-08-27 | 증발기 |
KR10-2015-0120913 | 2015-08-27 |
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Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR20050035551A (ko) * | 2003-10-13 | 2005-04-19 | 한라공조주식회사 | 열교환기 |
KR20090048352A (ko) * | 2007-11-09 | 2009-05-13 | 한라공조주식회사 | 열교환기 |
KR20130130297A (ko) * | 2012-05-22 | 2013-12-02 | 한라비스테온공조 주식회사 | 증발기 |
KR20140001537A (ko) * | 2012-06-27 | 2014-01-07 | 주식회사 고산 | 열교환기 |
JP2014513265A (ja) * | 2011-05-04 | 2014-05-29 | ハラ、ビステオン、クライメイト、コントロール コーポレーション | 蓄冷熱交換器 |
-
2015
- 2015-08-27 WO PCT/KR2015/008989 patent/WO2016032255A1/ko active Application Filing
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR20050035551A (ko) * | 2003-10-13 | 2005-04-19 | 한라공조주식회사 | 열교환기 |
KR20090048352A (ko) * | 2007-11-09 | 2009-05-13 | 한라공조주식회사 | 열교환기 |
JP2014513265A (ja) * | 2011-05-04 | 2014-05-29 | ハラ、ビステオン、クライメイト、コントロール コーポレーション | 蓄冷熱交換器 |
KR20130130297A (ko) * | 2012-05-22 | 2013-12-02 | 한라비스테온공조 주식회사 | 증발기 |
KR20140001537A (ko) * | 2012-06-27 | 2014-01-07 | 주식회사 고산 | 열교환기 |
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