Search

JP-2026076196-A - Heat exchanger, and heat pump comprising at least one heat exchanger.

JP2026076196AJP 2026076196 AJP2026076196 AJP 2026076196AJP-2026076196-A

Abstract

[Problem] The problem addressed by the present invention is to provide an improved heat exchanger that requires relatively little installation space and/or has improved efficiency, and an improved heat pump of the type described above. [Solution] At least one flow channel duct 8 is formed as a tubular conduit with a circular cross-section, and a plurality of rigid vortex-generating bodies 9 fixed in place are inserted into the flow channel duct 8 as internal components, and each of the plurality of vortex-generating bodies 9 has a central axis 10 in the middle portion that extends in the main flow direction 7 and a plurality of guide vanes 11 that extend radially outward from the central axis 10. [Selection Diagram] Figure 2

Inventors

  • カヴァディーニ，フィリップ
  • ローレンツ，マルティン
  • トマイディス，ディミトリオス

Assignees

  • シーメンス エナジー グローバル ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント コンパニー コマンディートゲゼルシャフト

Dates

Publication Date
20260511
Application Date
20260109
Priority Date
20211203

Claims (13)

  1. A heat exchanger (2, 4) having at least one vertically elongated flow channel duct (8), particularly a tubular heat exchanger, a tube bundle heat exchanger, a finned tubular heat exchanger and a plate heat exchanger (2, 4), During operation, the fluid flows through the main flow direction (7) which coincides with the longitudinal direction of the at least one flow path duct (8). The at least one flow channel duct (8) has internal components and/or structural features that impart vortices to the fluid flowing in the main flow direction (7) in the circumferential direction of the at least one flow channel duct (8), A heat exchanger characterized by (2, 4).
  2. A heat exchanger (2, 4) according to claim 1, The at least one flow channel duct (8) is formed as a tubular conduit with a circular cross-section, Multiple rigid vortex-generating bodies (9) fixed in place are inserted within the flow channel duct (8) as an internal component, and each of the multiple vortex-generating bodies (9) has a central axis (10) in the middle portion that extends in the main flow direction (7) and multiple guide vanes (11) that extend radially outward from the central axis (10). A heat exchanger characterized by (2, 4).
  3. A heat exchanger (2, 4) according to claim 1 or 2, The at least one vertically elongated flow channel duct (8) is formed as a tubular conduit, and the at least one vertically elongated flow channel duct (8) is at least partially divided into at least two partial ducts (8a, 8b) that extend parallel to each other in the main flow direction (7). A partition wall (13) extends between these partial ducts, and a baffle plate (14) is provided downstream of the first partial duct (8a) and upstream of the second partial duct (8b), extending laterally with respect to the main flow direction (7). The partition wall (13) is provided with a plurality of fluid passage openings (15), and the fluid introduced into the first partial duct (8a) is guided through the plurality of fluid passage openings (15) to the second partial duct (8b). A heat exchanger characterized by (2, 4).
  4. A heat exchanger (2, 4) according to claim 3, The at least one vertically elongated flow channel duct (8) is at least partially divided into three subducts (8a, b, c) that extend parallel to each other in the main flow direction (7). A partition wall (13) extends between them, and a baffle plate (14) is provided extending laterally with respect to the main flow direction (7) downstream of the first central partial duct (8a) and upstream of the second partial duct (8b) and the third partial duct (8c), respectively. The partition wall (13) is provided with a plurality of fluid flow openings (15), and the fluid introduced into the first partial duct (8a) is guided through the plurality of fluid flow openings (15) to the second partial duct (8b) and the third partial duct (8c) while being subjected to vortex flow. A heat exchanger characterized by (2, 4).
  5. A heat exchanger (2, 4) according to claim 4, The first partial duct (8a) has a rectangular or preferably square cross-section, and the second and third partial ducts (8b, c) each have a semicircular cross-section. A heat exchanger characterized by (2, 4).
  6. A heat exchanger (2, 4) according to any one of claims 3 to 5, The baffle plate (14) of the first partial duct (8a) is provided with at least one through hole (16), or preferably at least one through slit (17). A heat exchanger characterized by (2, 4).
  7. A heat exchanger (2, 4) according to any one of claims 3 to 6, The plurality of fluid passage openings (15) are spaced apart from each other in the main flow direction (7), and the distance between adjacent fluid passage openings (15) gradually increases towards the downstream direction. A heat exchanger characterized by (2, 4).
  8. A heat exchanger (2, 4) according to any one of claims 1 to 7, Multiple flow channel ducts (8) are provided, and each of the multiple flow channel ducts (8) extends in a linear main flow direction (7) and is connected to one another via multiple fluid flow openings (22), forming multiple flow channel duct sections, the flow channel sections overlap each other in the main flow direction (7) and are offset from each other in the lateral direction with respect to the main flow direction (7). Each of the plurality of flow channel ducts (8) through which the high-temperature fluid passes preferably has contact with an adjacent flow channel duct (8) through which the low-temperature fluid passes, along its entire length. A heat exchanger characterized by (2, 4).
  9. A heat exchanger (2, 4) according to claim 8, The flow channel duct section is formed by a plurality of rectangular parallelepiped hollow rods (23) having square end faces, and each free end of the end face is provided with one fluid flow opening (22). A heat exchanger characterized by (2, 4).
  10. A heat exchanger (2, 4) according to claim 9, The fluid passage opening (22) is formed in a slit shape and extends in the main flow direction (7), and its slit width (b) is 0.1 to 0.3 times, particularly 0.25 times, the length (d) of the end face of the hollow rod (23). A heat exchanger characterized by (2, 4).
  11. A heat exchanger (2, 4) according to claim 1, which takes the form of a finned plate heat exchanger, and has a plurality of flow path ducts (8), Each of the plurality of flow channel ducts (8) has a trapezoidal cross-section partitioned by two parallel plates (25) and diagonally arranged fins (26), and each of the flow channel ducts (8) is provided with a plurality of fluid flow openings (15) in at least one end wall. A heat exchanger characterized by (2, 4).
  12. A heat exchanger (2, 4) according to claim 11, On the side into which the fluid is introduced, each of the plurality of fluid passage openings (15) is provided with a hood (27) having an opening on the inflow side. A heat exchanger characterized by (2, 4).
  13. A heat pump (1) comprising at least one heat exchanger (2, 4) according to any one of claims 1 to 12.

Description

This invention relates to a heat exchanger. This heat exchanger has at least one elongated flow channel duct through which a fluid flows during operation in a main flow direction that coincides with the longitudinal direction of the flow channel duct. The invention further relates to a heat pump comprising at least one such heat exchanger. This type of heat exchanger is used, for example, in heat pump systems, and various embodiments are known in the prior art. In this case, various heat exchanger structures are used, such as tubular heat exchangers, multi-tube heat exchangers, finned-tube heat exchangers, and plate heat exchangers. One drawback of these heat exchangers is that they occupy a large installation space. Furthermore, currently, these methods only yield low COP (Coefficient of Performance) values. The COP value represents the efficiency of a heat pump system. It indicates the ratio of thermal output to the operating energy required to achieve it, and this operating energy is supplied to the heat pump system in the form of electricity. A schematic diagram of a heat pump.A perspective view of a flow channel duct formed according to the first approach of the present invention is shown. This flow channel duct can be used as the flow channel duct for the heat exchanger of the heat pump shown in Figure 1.Figure 2 shows an enlarged side view of the vortex generator, which is only schematically shown.A graph showing the improvement in heat transfer intensity of the modified flow channel duct shown in Figure 2, compared to the standard flow channel duct, as a function of the Reynolds number.Graphs showing the increase in flow friction loss for these modifications relative to the reference flow channel duct as a function of the Reynolds number.A graph showing the improvement in heat transfer intensity for these modifications relative to a standard flow channel duct when the Reynolds number is 10,000.A perspective view of a first modified example of a flow channel duct formed according to a second approach according to the present invention is shown. This flow channel duct can be used as a flow channel duct for the heat exchanger of the heat pump shown in Figure 1.A perspective view of a second modified example of a flow channel duct formed according to a second approach according to the present invention is shown. This flow channel duct can be used as a flow channel duct for the heat exchanger of the heat pump shown in Figure 1.A perspective view of a third modified example of a flow channel duct formed according to the second approach of the present invention is shown. This flow channel duct can be used as a flow channel duct for the heat exchanger of the heat pump shown in Figure 1.Figure 7 shows a perspective view of the first modified example, which, as an example, illustrates the reversal of direction of a fluid guided through a flow channel duct.Graphs showing the improvement in heat transfer intensity relative to the standard flow channel duct as a function of the Reynolds number for the modified examples illustrated in Figures 7-9.Graphs showing the increase in flow friction loss as a function of the Reynolds number for the modified examples shown in Figures 7-9 relative to the standard flow channel duct.Graphs showing the improvement in heat transfer intensity to the standard flow channel duct for the modified examples shown in Figures 7-9, when the Reynolds number is 10,000.Figure 1 shows a perspective view of a heat exchanger that can be used as a heat exchanger for the heat pump shown. These flow ducts are formed according to a third approach according to the present invention.A cross-sectional view along line XV in Figure 14.A partially perspective view of the heat exchanger shown in Figure 14.Schematic diagram of the two flow path ducts of the heat exchanger shown in Figure 14.A graph showing the improvement in heat transfer intensity of three modified flow channel ducts, as a function of the Reynolds number, compared to the standard flow channel duct, for each of the three modified flow channel ducts shown in Figure 17.A graph showing the increase in flow friction loss as a function of the Reynolds number for three modified flow channel ducts shown in Figure 17, compared to the standard flow channel duct.A graph showing the improvement in heat transfer intensity compared to the standard flow channel duct for three modified flow channel ducts shown in Figure 17, when the Reynolds number is 10,000.A perspective view of a first modified flow channel duct formed according to a first modification of a fourth approach according to the present invention is shown. This flow channel duct can be used as a flow channel duct for the heat exchanger of the heat pump shown in Figure 1.Figure 21 is a front view of the flow channel duct, illustrating the change in direction of the fluid guided through this duct.A perspective view of a second modified example of a flow channel duct formed according to a four