EP2071266A1 - Tube ondulé pour échangeur thermique destiné à une alimentation en eau chaude - Google Patents

Tube ondulé pour échangeur thermique destiné à une alimentation en eau chaude Download PDF

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Publication number
EP2071266A1
EP2071266A1 EP07792965A EP07792965A EP2071266A1 EP 2071266 A1 EP2071266 A1 EP 2071266A1 EP 07792965 A EP07792965 A EP 07792965A EP 07792965 A EP07792965 A EP 07792965A EP 2071266 A1 EP2071266 A1 EP 2071266A1
Authority
EP
European Patent Office
Prior art keywords
heat transfer
projections
transfer tube
corrugated
hot water
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP07792965A
Other languages
German (de)
English (en)
Other versions
EP2071266A4 (fr
Inventor
Zhixing Li
Jian Meng
Mitsuharu Numata
Kazushige Kasai
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Tsinghua University
Daikin Industries Ltd
Original Assignee
Tsinghua University
Daikin Industries Ltd
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Publication date
Application filed by Tsinghua University, Daikin Industries Ltd filed Critical Tsinghua University
Publication of EP2071266A1 publication Critical patent/EP2071266A1/fr
Publication of EP2071266A4 publication Critical patent/EP2071266A4/fr
Withdrawn legal-status Critical Current

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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
    • F28F1/30—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 attachable to the element
    • 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
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/02—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled
    • 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
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • 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
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/424—Means comprising outside portions integral with inside portions
    • F28F1/426—Means comprising outside portions integral with inside portions the outside portions and the inside portions forming parts of complementary shape, e.g. concave and convex
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation

Definitions

  • the present invention relates to hot water heater technology. More specifically, the present invention relates to a hot water corrugated heat transfer tube in which the Reynolds number Re of a fluid flowing inside the tube is less than 7,000.
  • Heat exchangers used in air conditioners, hot water heaters, and the like are provided with a heat transfer tube in which a fluid such as water flows and which exchanges heat due to the temperature differential between the tube interior and exterior. Furthermore, to improve the heat transfer performance of the heat transfer tube, a grooved tube in which grooves are formed on the tube inner surface is used in some cases. In addition, a technology has also been proposed which improves the heat transfer performance by providing projections on the inner surface of the heat transfer tube.
  • Patent Document 1 Providing projections inside the heat transfer tube in this manner increases the heat transfer surface area of the heat transfer tube and agitates the fluid, thereby increasing the heat transfer coefficient of the heat transfer surface and improving the heat transfer performance.
  • Patent Document 2 a technology has been proposed that provides projections 0.45 - 0.6 mm in height inside the heat transfer tube, thereby suppressing the pressure loss while promoting the transfer of heat with the refrigerant.
  • Patent Document 2 a technology that improves the heat transfer performance by employing a corrugated heat transfer tube has been also suggested.
  • the water is heated in a single pass from approximately 10° C to approximately 90° C over a long period of time in order to efficiently utilize inexpensive nighttime electric power.
  • the flow volume of the water flowing inside the heat transfer tube is set to an extremely small value (e.g., 0.8 L/min) in order to make the product compact and to ensure high efficiency.
  • a method is employed that improves the heat transfer performance by reducing the inner diameter of the heat transfer tube and thereby increasing the flow speed inside the tube.
  • efficient heat exchange cannot be expected because the thermal conductivity is also small in the low temperature section in the vicinity of the water inlet.
  • the improvement in the heat transfer performance simply by means of the corrugated tube is small.
  • the corrugated tube causes a strong turbulence at the boundary of the tube wall, the friction factor inside the tube increases considerably compared to a smooth tube depending on the depth of the corrugated groove, which consequently increases the pressure loss of the flow inside the tube.
  • a hot water corrugated heat transfer tube is a hot water corrugated heat transfer tube that exchanges heat between its interior and exterior, in which a plurality of projections each having a height H1 of 0.5 - 1.5 mm is provided in at least one part of the inner surface of a portion positioned in a section where the Reynolds number Re of a fluid flowing in the interior is less than 7,000.
  • a plurality of projections that protrude toward the inside of the tube and have a height of 0.5 - 1.5 mm is provided on the inner surface of the portion positioned in the low Reynolds number section where the laminar flow zone is produced and the transition from the laminar flow zone to the turbulent flow zone occurs, i.e., in the section where the Reynolds number Re is less than 7,000.
  • the projections provided inside the corrugated tube and the tube improve the heat transfer coefficient, the depth of the corrugated grooves is reduced, and the impact of the projections on the pressure loss inside the tube is small, thereby improving the performance of the entire hot water corrugated heat transfer tube.
  • a hot water corrugated heat transfer tube is a hot water corrugated heat transfer tube that exchanges heat between its interior and exterior, in which a plurality of projections each whose height H1 is 0.05 - 0.15 times an inner diameter D is provided in at least one part of the inner surface of a portion positioned in a section where the Reynolds number Re of a fluid flowing in the interior is less than 7,000.
  • the friction factor inside the tube is a function of the Reynolds number Re and the relative roughness.
  • the ratio of the height of the projections provided inside the tube to the tube inner diameter i.e., the relative roughness
  • a plurality of projections each whose height H1 is 0.05 - 0.15 times the inner diameter D is provided on the inner surface of the portion positioned in the low Reynolds number section where the laminar flow zone is produced and the transition from the laminar flow zone to the turbulent flow zone occurs, i.e., in the section where the Reynolds number Re is less than 7,000.
  • the projections provided inside the tube improve the heat transfer coefficient, and reduce the impact of the projections on the pressure loss inside the tube, thereby improving the performance of the entire hot water corrugated heat transfer tube.
  • a hot water corrugated heat transfer tube is a heat transfer tube used in a heat exchanger of a hot water heater and configured to exchange heat between its interior and exterior, in which a plurality of projections each whose height (H1) is in the range of 1 - 3 times the depth (Hm) of the corrugated grooves is provided in at least one part of the inner surface of a portion positioned in a section where the Reynolds number (Re) of a fluid flowing in the interior is less than 7,000.
  • the projections are provided in the heat transfer tube in which the corrugated grooves are provided, it is necessary to improve the heat transfer effect by the height (H1) of the projections and the depth (Hm) of the corrugated grooves and also minimize the impact caused by the pressure loss.
  • the height (H1) of the plurality of projections is in the range of 1 - 3 times the depth (Hm) of the corrugated grooves
  • the corrugated tube and the projections provided inside the tube improve the heat transfer coefficient, the depth of the corrugated grooves is reduced, and the impact of the projections on the pressure loss inside the tube is small, thereby improving the performance of the entire hot water corrugated heat transfer tube.
  • a hot water corrugated heat transfer tube is a heat transfer tube used in a heat exchanger of a hot water heater and configured to exchange heat between its interior and exterior, in which a plurality of projections is provided in at least one part of the inner surface of a portion positioned in a section where the Reynolds number (Re) of a fluid flowing in the interior is less than 7,000, and the value of the pitch (P1) of the plurality of projections is different from the value of the pitch (Pm) of the corrugated grooves.
  • a hot water corrugated heat transfer tube is a heat transfer tube used in a heat exchanger of a hot water heater and configured to exchange heat between its interior and exterior, in which a plurality of projections each whose height H1 is 0.5 - 1.5 mm is provided on the inner surface of a portion positioned in the vicinity of an inlet into which water, which is the fluid flowing in the interior, flows.
  • the flow of the water in the vicinity of the inlet of the heat transfer tube used in the hot water heat exchanger corresponds to the laminar flow zone and/or the transition zone where the flow transitions from the laminar flow zone to the turbulent flow zone.
  • the water temperature in the vicinity of the inlet of the heat transfer tube is low, and the heat transfer coefficient is also low.
  • a plurality of projections each having a height of 0.5 - 1.5 mm is provided on the inner surface of the portion positioned at least in the vicinity of the water inlet, thereby improving the heat transfer coefficient due to the projections provided inside the tube.
  • the impact of the projections on the pressure loss inside the tube is small, thereby improving the performance of the entire hot water corrugated heat transfer tube.
  • a hot water corrugated heat transfer tube is a heat transfer tube used in a heat exchanger of a hot water heater and configured to exchange heat between its interior and exterior, in which a plurality of projections each whose height H1 is 0.05 - 0.15 times the inner diameter D is provided on the inner surface of a portion positioned in the vicinity of a fluid inlet into which water, which is the fluid flowing in the interior, flows.
  • the flow of the water in the vicinity of the inlet of the heat transfer tube corresponds to the laminar flow zone and/or the transition zone where the flow transitions from the laminar flow zone to the turbulent flow zone.
  • the water temperature in the vicinity of the inlet of the heat transfer tube is low, and the heat transfer coefficient is also low.
  • a plurality of projections each whose height is 0.05 - 0.15 times the heat transfer tube inner diameter is provided on the inner surface of the heat transfer tube positioned at least in the vicinity of the water inlet.
  • a hot water corrugated heat transfer tube is a heat transfer tube used in a heat exchanger of a hot water heater and configured to exchange heat between its interior and exterior, in which a plurality of projections each whose height (H1) is in the range of 1 - 3 times the depth (Hm) of the corrugated grooves is provided on the inner surface of the portion positioned in the vicinity of an inlet into which water, which is the fluid flowing in the interior, flows.
  • the flow of the water in the vicinity of the inlet of the heat transfer tube corresponds to the laminar flow zone and/or the transition zone where the flow transitions from the laminar flow zone to the turbulent flow zone.
  • the water temperature in the vicinity of the inlet of the heat transfer tube is low, and the heat transfer coefficient is also low.
  • the projections are provided inside the heat transfer tube in which the corrugated grooves are provided in order to improve the heat transfer coefficient.
  • the projections are provided in the heat transfer tube in which the corrugated grooves are provided, it is necessary to improve the heat transfer effect by the height (H1) of the projections and the depth (Hm) of the corrugated grooves and also minimize the impact caused by the pressure loss.
  • a hot water corrugated heat transfer tube is a heat transfer tube used in a heat exchanger of a hot water heater and configured to exchange heat between its interior and exterior, in which a plurality of projections is provided on the inner surface of the portion positioned in the vicinity of an inlet into which water, which is the fluid flowing in the interior, flows, and the value of the pitch (P1) of the plurality of projections is different from the value of the pitch (P2) of the corrugated grooves.
  • the flow of the water in the vicinity of the inlet of the heat transfer tube corresponds to the laminar flow zone and/or the transition zone where the flow transitions from the laminar flow zone to the turbulent flow zone.
  • the water temperature in the vicinity of the inlet of the heat transfer tube is low, and the heat transfer coefficient is also low.
  • the projections are provided inside the heat transfer tube in which the corrugated grooves are provided in order to improve the heat transfer coefficient.
  • the projections and the corrugated grooves are provided at positions where they overlap each other, the friction factor inside the tube increases and there is a risk that the pressure loss inside the tube rapidly increases.
  • a hot water corrugated heat transfer tube is the hot water corrugated heat transfer tube according to any one of the first aspect through the eighth aspect of the invention, in which the flow speed of the fluid flowing in the interior is 0.1 - 0.6 m/s. Furthermore, it is preferable that the flow speed of the fluid flowing inside the hot water corrugated heat transfer tube is 0.2 - 0.4 m/s.
  • the flow speed of the fluid inside the tube is less than 0.1 m/s, the heat transfer coefficient of the corrugated heat transfer tube is extremely low.
  • the flow speed of the fluid inside the corrugated tube exceeds 0.6 m/s, the friction factor inside the corrugated tube increases and the pressure loss inside the tube increases.
  • the range of the flow speed of the fluid flowing in the interior is set to 0.1 - 0.6 m/s.
  • a hot water corrugated heat transfer tube is the hot water corrugated heat transfer tube according to any one of the first aspect through the eighth aspect of the invention, in which the cross sectional shape at an arbitrary height of each projection is a smooth curve like a circle, an ellipse, or an approximate circle.
  • Examples of factors that influence the pressure loss of the fluid inside the tube due to the projections inside the corrugated tube include the height of the corrugated grooves, the Reynolds number and flow speed of the fluid inside the tube, the height of the projections, as well as the shape of the projections.
  • the projections are acute angle shaped, separation vortices are generated by the flow rounding the angle, which increases the pressure loss of the fluid.
  • the cross sectional shape at an arbitrary height of a projection comprises a smooth curve, such as a circle, an ellipse, or an approximate circle.
  • the outer circumferential surface of the projections are formed with a smooth curved surface, the generation of separation vortices can be suppressed compared with projections that are acute angle shaped, and the impact of the loss of pressure of the fluid inside the tube is suppressed, thereby improving the performance of the entire corrugated heat transfer tube.
  • a hot water corrugated heat transfer tube is the hot water corrugated heat transfer tube according to any one of the first aspect through the eighth aspect of the invention, in which the projections are not provided in a section positioned in the vicinity of a fluid outlet out of which the fluid flows.
  • a hot water corrugated heat transfer tube is the hot water corrugated heat transfer tube according to any one of the first aspect through the eighth aspect of the invention, in which grooves each having a depth shallower than the height H1 of each projection are formed on the tube inner surface.
  • the large projections contribute more to the improvement in the heat transfer coefficient than the small projections. Accordingly, providing inside the corrugated heat transfer tube projections each whose height is greater than the depth of grooves in a grooved tube improves the heat transfer effect.
  • grooves shallower than the height of the projections contribute more to the improvement in the heat transfer coefficient. Accordingly, in the high Reynolds zone, the heat transfer performance of the corrugated heat transfer tube is further improved by the usage of the grooved tube in which grooves shallower than the height of the projections are formed on the inner surface.
  • a hot water corrugated heat transfer tube is the hot water corrugated heat transfer tube according to any one of the first aspect through the eighth aspect of the invention in which the plurality of projections is provided parallel to the tube axial direction.
  • the promotion of heat transfer is performed in a continuous manner.
  • the additional pressure loss is small, thereby improving the performance of the entire heat transfer tube.
  • a hot water corrugated heat transfer tube is the hot water corrugated heat transfer tube according to any one of the first aspect through the eighth aspect of the invention, in which the plurality of projections is helically provided.
  • Helically providing the projections generates a turning in the flow of the fluid inside the tube, and increases the length of the passage of the fluid, thereby further increasing the heat transfer performance.
  • a hot water corrugated heat transfer tube is the hot water corrugated heat transfer tube according to any one of the first aspect through the eighth aspect of the invention, in which the plurality of projections is provided such that they are paired at opposing positions in the radial direction of the heat transfer tube.
  • Providing projections such that they form pairs at opposing positions in the radial direction reduces the cross sectional area in the vicinity of the projections, promotes the mixing of the fluid, and further improves the heat transfer performance.
  • a hot water corrugated heat transfer tube is the hot water corrugated heat transfer tube according to any one of the first aspect through the eighth aspect of the invention, in which the ratio of a pitch P1 of the plurality of projections to the heat transfer tube inner diameter D is 0.5 - 10.
  • a hot water corrugated heat transfer tube according to a seventeenth invention is the hot water corrugated heat transfer tube according to any one of the first aspect through the eighth aspect of the invention, in which small projections each whose height (H2) is less than 0.5 mm are provided between the plurality of projections.
  • the large projections contribute more to the improvement in the heat transfer coefficient than the small projections
  • the small projections contribute more to the improvement in the heat transfer coefficient than the large projections. Accordingly, providing small projections between the large projections achieves a synergistic effect in that the heat transfer performance due to the large projections is improved in the section where the Reynolds number is low, and the heat transfer performance due to the small projections is improved in the section where the Reynolds number is high, thereby improving the performance of the entire heat exchanger.
  • a hot water corrugated heat transfer tube according to an eighteenth invention is the hot water corrugated heat transfer tube according to any one of the first aspect through the eighth aspect of the invention, in which a smooth part not provided with projections exists on the inner surface of the heat transfer tube.
  • the cross sectional area inside the heat transfer tube is maximal.
  • the effect is the same as that obtained in a heat transfer tube whose inner diameter is reduced, i.e., the flow speed of the fluid increases and the heat transfer is promoted, but the pressure loss inside the tube increases.
  • a hot water corrugated heat transfer tube is the hot water corrugated heat transfer tube according to any one of the first aspect through the eighth aspect of the invention, in which the projections are formed by the application of force from the exterior, are formed in a linear part, and are not formed in a bent part.
  • the heat transfer tube generally has a linear part and a bent part.
  • An additional pressure loss due to bending exists in the bent part besides the pressure loss in the linear part.
  • the bending work process creates a large deformation in the depressed region of the outer surface of the heat transfer tube, which creates a risk of breakages, and the like. Therefore, the projections are provided in the linear part, and projections are not provided in the bent part.
  • a hot water corrugated heat transfer tube is the hot water corrugated heat transfer tube according to any one of the first aspect through the eighth aspect of the invention, in which the projections are formed by the application of force from the exterior, and are not formed in a section that intersects the bent surface in the bent part.
  • the amount of deformation is greatest in the portion that intersects the bent surface. Therefore, in the bent part of the heat transfer tube, projections are not provided in the section that intersects the bent surface. For example, when the heat transfer tube is bent at a horizontal surface, projections are not provided at the section that intersects the horizontal surface in the bent part.
  • a hot water corrugated heat transfer tube is the hot water corrugated heat transfer tube according to any one of the first aspect through the eighth aspect of the invention, in which a second heat transfer tube is disposed in the exterior to flow a second fluid that supplies heat to the fluid; the second heat transfer tube contacts an outer surface; and the projections are formed on the inner surface by depressing the outer surface, and are formed at a location outside of the portion that contacts the second heat transfer tube.
  • the projections are formed on the inner surface by depressing the outer surface, and depressions are consequently formed on the outer surface corresponding to the region where the projections are formed on the inner surface. Projections are formed at the portion that contacts the second heat transfer tube. In other words, when depressions are formed on the outer surface, the contact between the heat transfer tube and the second heat transfer tube worsens, thereby reducing the heat transfer effect from the second heat transfer tube. Therefore, by not providing projections in the section of contact with the second heat transfer tube, it is possible to prevent a reduction in the effect of transferring heat from the second heat transfer tube.
  • FIG. 1 is a schematic diagram of a heat pump type hot water heater that uses a hot water corrugated heat transfer tube of the present invention.
  • the heat pump type hot water heater comprises a hot water supply unit 1, and a heat pump unit 2.
  • the following are successively connected in the hot water supply unit 1: a service water tube 11, a hot water storage tank 12, a water circulation pump 13, a water supply tube 3, a corrugated heat transfer tube 31 that constitutes a water heat exchanger 30, a hot water tube 16, a mixing valve 17, and a hot water supply tube 18.
  • service water is supplied from the water supply tube 11 to the hot water storage tank 12.
  • Low temperature water is supplied by the water circulation pump 13 from the bottom part of the hot water storage tank 12 to the corrugated heat transfer tube 31 of the water heat exchanger 30, and heated.
  • the heated hot water flows into the upper part of the hot water storage tank 12.
  • the high temperature hot water that exits from the upper part of the hot water storage tank 12 via the hot water tube 16 is mixed with the cold water of a mixed water tube 19 by the mixing valve 17.
  • This mixing valve 17 regulates the temperature of the supplied hot water, which is supplied to the user by the hot water supply tube 18.
  • the heat pump unit 2 is provided with a refrigerant circulation circuit that comprises a compressor 21, the water heat exchanger 30, an expansion valve 23, and an air heat exchanger 24, which are connected sequentially by a refrigerant tube 32.
  • the refrigerant is compressed to a high pressure by the compressor 21, and is then sent to the water heat exchanger 30.
  • the refrigerant whose heat was exchanged in the water heat exchanger 30 passes through the expansion valve 23, and is supplied to the air heat exchanger 24.
  • the refrigerant absorbs heat from the surroundings, and then is circulated back to the compressor 21.
  • FIG 2 is a schematic diagram of the water heat exchanger 30 in the heat pump type hot water heater.
  • the water heat exchanger 30 comprises the corrugated heat transfer tube 31 and the refrigerant tube 32.
  • the corrugated heat transfer tube 31 is spirally formed in the same plane so as to be an oval shape, and forms a water passageway W.
  • the refrigerant tube 32 is helically wound around the outer circumference of the heat transfer tube 31, and forms a refrigerant passageway R.
  • the outer circumferential side of the spiral shaped corrugated heat transfer tube 31 is a water inlet 311, and the center side of the spiral shaped corrugated heat transfer tube 31 is a water outlet 312.
  • the refrigerant inside the refrigerant tube 32 flows into the refrigerant inlet 322 in the A22 direction, and radiates heat. Subsequently, the refrigerant flows out of the refrigerant outlet 321 in the A21 direction.
  • the service water supplied into the water inlet 311 in the A11 direction is heated by this heat, turns into hot water, and flows out of the water outlet 312 in the A12 direction.
  • the corrugated heat transfer tube 31 is described. As shown in Figure 3 , on the tube inner surface of the corrugated heat transfer tube 31, corrugated grooves 316 are formed and a plurality of projections 313 each having a height H1 is provided vertically symmetric in the tube axial direction. In Figure 3 , only the projections 313 are provided upward when viewed from the paper surface are shown.
  • the water temperature at the water inlet 311 of the heat transfer tube 31 is set to approximately 10° C
  • the water temperature at the water outlet 312 is set to approximately 90° C.
  • the flow volume of the water in the corrugated heat transfer tube is approximately 0.8 L/min.
  • the outer diameter of the corrugated heat transfer tube is preferably 8.0 - 14.0 mm (inner diameter is 6.0 - 12.0 mm).
  • Figure 4 is a chart of the Reynolds number Re of the flow inside the corrugated heat transfer tube 31.
  • the Reynolds number Re at the water inlet 311 of the corrugated heat transfer tube 31 is approximately 2,000, and the flow inside the tube is in the laminar flow zone.
  • the Reynolds number Re at the water outlet 312 is approximately 7,000, and the flow inside the tube is in the transition zone where the flow transitions from laminar flow to turbulent flow.
  • Figure 5(a) is a cross sectional perspective view of the corrugated heat transfer tube 31.
  • projections each having the height H1 are provided vertically symmetric on the tube inner surface having an inner diameter D of 8.0 mm in which the corrugated grooves 316 having a depth of Hm are provided.
  • Figure 5(b) is a cross sectional view taken along the A-A arrow in Figure 5(a)
  • Figure 5(c) is a cross sectional view taken along the B-B arrow in Figure 5(b) .
  • the projections 313 are formed on the inner surface by depressing the outer surface of the heat transfer tube.
  • each projection 313 is formed such that its shape in the transverse sectional view is elliptical.
  • flat surfaced parts 31 a not provided with projections exist on the inner surface of the corrugated heat transfer tube 31.
  • Figure 6(a) graphs, for each Reynolds number Re in the low Reynolds number section where the laminar flow zone is produced and the transition of the flow inside the tube from the laminar flow zone to the turbulent flow zone occurs, the heat transfer performance in the case of using a corrugated tube not provided with projections and in the case of using a corrugated tube in which the depth of the corrugated grooves is Hm and the height H1 of the projections is 1.2 mm.
  • the horizontal axis represents the value of the Reynolds number Re.
  • the vertical axis represents the ratio (Nu/Nuo), which is the ratio of the Nusselt number Nu of the corrugated heat transfer tube provided with the projections 313 and the corrugated heat transfer tube not provided with projections to the Nusselt number Nuo of the smooth heat transfer tube.
  • Nusselt number is the heat transfer coefficient converted to a dimensionless number, which serves as an index of how easily heat transfers from the solid wall to the fluid: the larger that number, the easier that heat conducts from the solid wall to the fluid. Accordingly, the larger the Nu/Nuo value, the greater the improvement in the heat transfer performance of the heat transfer tube due to the projections and corrugated grooves.
  • the solid line represents the experimental results in the case of using the corrugated heat transfer tube provided with the projections 313, and the dotted line represents the experimental results in the case of using the corrugated heat transfer tube not provided with the projections.
  • the heat transfer performance of the corrugated heat transfer tube not provided with the projections is approximately three times that of the smooth tube, regardless of the Reynolds number.
  • the Reynolds number Re is equal to or less than 4,000
  • the improvement in the heat transfer performance due to the projections 313 provided inside the tube is clear.
  • the Reynolds number Re is equal to or greater than 4,000
  • the improvement in the heat transfer performance due to the projections 313 provided inside the tube is modest.
  • Figure 6(b) graphs, for each Reynolds number Re in the low Reynolds number section where the laminar flow zone is produced and the transition of the flow inside the tube from the laminar flow zone to the turbulent flow zone occurs, the trend in the pressure loss inside the tube in the case of using a corrugated tube not provided with projections and in the case of using the corrugated heat transfer tube 31 whose depth of the corrugated grooves is Hm and the height H1 of the projections is 1.2 mm.
  • the horizontal axis represents the value of the Reynolds number Re.
  • the vertical axis represents the ratio (f/fo), which is the ratio of the Fanning friction factor f of the corrugated heat transfer tube provided with the projections 313 and the corrugated heat transfer tube not provided with projections to the Fanning friction factor fo of the smooth tube.
  • the Fanning friction factor is a dimensionless number that indicates the pressure loss of the flow inside the tube: the larger that number, the greater the pressure loss of the flow inside the tube. Accordingly, the larger the f/fo value, the greater the water pressure loss inside the tube.
  • the solid line represents the experimental results in the case of using the corrugated heat transfer tube provided with the projections 313, and the dotted line represents the experimental results in the case of using the corrugated heat transfer tube not provided with the projections. As shown in Figure 6(b) , when the Reynolds number Re is equal to or less than 7,000, the increase of the pressure loss due to the projections 313 provided on the tube inner surface is substantially stable.
  • FIG. 7(a) graphs the heat transfer performance for the case where projections having differing heights H1 are provided vertically symmetric in a corrugated heat transfer tube having an inner diameter D of 8.0 mm such that the pitch P in the tube axial direction is 15 mm.
  • the horizontal axis represents the value of the height H1 of the projections 313.
  • the vertical axis represents the ratio (Nu/Nuo), which is the ratio of the Nusselt number Nu of the corrugated heat transfer tube 31 provided with the projections 313 to the Nusselt number Nuo of the smooth tube not provided with projections.
  • the solid line represents the experimental results for the case where the Reynolds number Re is 4,000
  • the dotted line represents the experimental results for the case where the Reynolds number Re is 2,000.
  • Figure 7(b) graphs the trend in the pressure loss inside the tube.
  • the horizontal axis represents the value of the height H1 of the projections 313.
  • the vertical axis represents the ratio (f/fo), which is the ratio of the Fanning friction factor f of the corrugated heat transfer tube 31 provided with the projections 313 to the Fanning friction factor fo of the smooth tube not provided with projections.
  • the solid line represents the experimental results for the case where the Reynolds number Re is 4,000
  • the dotted line represents the experimental results for the case where the Reynolds number Re is 2,000.
  • the greater the height H1 of the projections 313, the greater the pressure loss inside the tube, for both the case where the Reynolds number Re is 4,000 and 2,000.
  • the ratio H1 is equal to or greater than 1.0, an increase in the pressure loss inside the tube is remarkable.
  • Figure 7(c) graphs the performance of the entire heat transfer tube for the case where projections having differing heights H1 were provided vertically symmetric at a 15.0 mm pitch (in the tube axial direction) in a corrugated heat transfer tube having the inner diameter D of 8.0 mm.
  • the performance comprehensively taking into consideration the improvement in the heat transfer performance and the suppression of the pressure loss is represented.
  • the horizontal axis represents the value of the height of the projections.
  • the vertical axis represents the value of the ratio (Nu/Nuo), which is the ratio of the Nusselt number Nu of the corrugated heat transfer tube provided with projections to the Nusselt number Nuo of the smooth tube not provided with projections, divided by the ratio (f/fo), which is the ratio of the Fanning friction factor f of the heat transfer tube provided with projections to the Fanning friction factor fo of the smooth tube not provided with projections.
  • Nu/Nuo the ratio of the Nusselt number Nu of the corrugated heat transfer tube provided with projections to the Nusselt number Nuo of the smooth tube not provided with projections
  • f/fo the ratio of the Fanning friction factor f of the heat transfer tube provided with projections to the Fanning friction factor fo of the smooth tube not provided with projections.
  • the solid line represents the experimental results for the case where the Reynolds number Re is 4,000
  • the dotted line represents the experimental results for the case where the Reynolds number Re is 2,000.
  • the value of Nu/Nuo divided by f/fo is largest.
  • the height of the projections exceeds 2.0 mm, the value decreases remarkably.
  • the performance of the entire heat transfer tube improves when the height of the projections is in the range of 0.5 - 1.5 mm.
  • it is preferable that the height of the projections is in the range of 0.5 - 0.79 mm.
  • the vertical axis represents the ratio (Nu/Nuo), which is the ratio of the Nusselt number Nu of the corrugated heat transfer tube 31 provided with the projections 313 to the Nusselt number Nuo of the smooth heat transfer tube not provided with projections.
  • the larger the value of the relative roughness (H1/D) of the projections the greater the improvement in the heat transfer performance.
  • the projections yield little improvement in the heat transfer performance when the value of the relative roughness (H1/D) is equal to or less than 0.1.
  • Figure 8(b) graphs the trend in the pressure loss inside the tube.
  • the horizontal axis represents the value of the relative roughness (H1/D).
  • the vertical axis represents the ratio (f/fo), which is the ratio of the Fanning friction factor f of the corrugated heat transfer tube 31 provided with the projections 313 to the Fanning friction factor fo of the smooth tube not provided with projections.
  • the solid line represents the experimental results for the case where the Reynolds number Re is 4,000
  • the dotted line represents the experimental results for the case where the Reynolds number Re is 2,000.
  • the ratio H1/D is equal to or greater than 0.12, an increase in the pressure loss inside the tube is remarkable.
  • Figure 8(c) graphs the heat transfer performance of the entire corrugated heat transfer tube by varying the relative roughness (H1/D) of the projections.
  • the horizontal axis represents the value of the relative roughness (H1/D).
  • the vertical axis represents the value of the ratio (Nu/Nuo), which is the ratio of the Nusselt number Nu of the heat transfer tube provided with projections to the Nusselt number Nuo of the smooth tube not provided with projections, divided by the ratio (f/fo), which is the ratio of the Fanning friction factor f of the corrugated heat transfer tube provided with projections to the Fanning friction factor fo of the smooth tube not provided with projections.
  • the larger the Nu/Nuo value the greater the improvement in the heat transfer performance; and the larger the f/fo value, the greater the water pressure loss inside the tube. Accordingly, the larger the value of Nu/Nuo divided by f/fo, the greater the improvement in the heat transfer coefficient, the smaller the impact of the projections on the pressure loss inside the tube, and the greater the improvement in the performance of the entire corrugated heat transfer tube.
  • the vertical axis represents the ratio (Nu/Nuo), which is the ratio of the Nusselt number Nu of the corrugated heat transfer tube 31 provided with the projections 313 to the Nusselt number Nuo of the smooth tube not provided with projections.
  • the larger the value of the relative height (H1/Hm) of the projections the greater the improvement in the heat transfer performance.
  • the projections yield little improvement in the heat transfer performance when the value of the relative height (H1/Hm) is equal to or less than 0.5.
  • Figure 9(b) graphs the trend in the pressure loss inside the tube.
  • the horizontal axis represents the value of the relative height (H1/Hm).
  • the vertical axis represents the ratio (f/fo), which is the ratio of the Fanning friction factor f of the corrugated heat transfer tube 31 provided with the projections 313 to the Fanning friction factor fo of the smooth tube not provided with projections.
  • the solid line represents the experimental results for the case where the Reynolds number Re is 4,000
  • the dotted line represents the experimental results for the case where the Reynolds number Re is 2,000.
  • the ratio H1/Hm is equal to or greater than 1.8, an increase in the pressure loss inside the tube is remarkable.
  • Figure 9(c) graphs the heat transfer performance of the entire heat transfer tube by varying the relative height (H1/Hm) of the projections.
  • the horizontal axis represents the value of the relative height (H1/Hm).
  • the vertical axis represents the value of the ratio (Nu/Nuo), which is the ratio of the Nusselt number Nu of the heat transfer tube provided with projections to the Nusselt number Nuo of the smooth tube not provided with projections, divided by the ratio (f/fo), which is the ratio of the Fanning friction factor f of the heat transfer tube provided with projections to the Fanning friction factor fo of the smooth tube not provided with projections.
  • the following embodiments further describe structures that differ from the hot water corrugated heat transfer tube according to the present invention (in the following embodiments, values such as the inner diameter D, the depth Hm of the corrugated grooves, the heights H1, H2 and the pitch of the projections, and the depths of the grooves, are merely for illustrative purposes, and it is also possible to use in these embodiments the values used in the abovementioned experiments, as well as the numerical ranges of the various parameters described in the claims).
  • FIG 10 shows the structure of a corrugated heat transfer tube 41 used in Experiment 1.
  • corrugated grooves 416 each having a groove depth Hm of 0.5 mm and the pitch Pm in the tube axial direction of 10.0 mm is provided on a smooth tube whose diameter D is 8.0 mm.
  • projections 43 each having a height H1 of 1.0 mm are provided vertically symmetric such that the pitch P in the tube axial direction is 15.0 mm.
  • corrugated grooves 516 are provided and small projections 515 each having a height H2 of 0.3 mm are provided between projections 513 each having a height H1 of 1.0 mm.
  • the large projections contribute to the improvement in the heat transfer coefficient more than the small projections
  • the small projections contribute to the improvement in the heat transfer coefficient more than the large projections.
  • the small projections 515 each whose height H2 is 0.3 mm between the projections 513 each whose height H1 is 1.0 mm, a synergistic effect is achieved in that the corrugated groove 516 and the projections 513 improve the heat transfer performance in the section where the Reynolds number is low, and the corrugated grooves 516 and the small projections 515 improve heat transfer performance in the section where the Reynolds number is high, thereby improving the performance of the entire heat exchanger.
  • a corrugated heat transfer tube 61 employed in a third embodiment is provided with projections 613 along a helix C1 on the tube inner surface.
  • Figure 12(a) is a plan view of the corrugated heat transfer tube 61
  • Figure 12(b) is a perspective view of the corrugated heat transfer tube 61.
  • the height H1 of the projections 613 is 1.0 mm
  • a pitch P1 in the circumferential direction is 6.0 mm
  • a pitch P2 in the tube axial direction is 6.0 mm.
  • a corrugated heat transfer tube 63 employed in a fourth embodiment comprises a section 63a provided with projections 633, and a section 63b not provided with projections, on a heat transfer tube provided with corrugated grooves 636 having a depth of 0.5 mm.
  • the section 63b not provided with projections is positioned in the vicinity of a water outlet 632.
  • the temperature of the waster, which is a fluid is high in the vicinity of the outlet 632 of the heat transfer tube 63, and there is therefore a risk of scaling of the tube wall.
  • projection parts are provided in such a section, it may promote scaling. Therefore, scaling is suppressed by not providing projections in the section 63b positioned in the vicinity of the water outlet 632, where the water temperature is high.
  • a corrugated heat transfer tube 64 employed in a fifth embodiment is a grooved tube provided with corrugated grooves 646 each having a depth of 0.5 mm and grooves 644 each having a depth of 0.2 mm, in which projections 643 each having a height H1 of 1.0 mm are provided vertically symmetric such that their pitch P in the tube axial direction is 15.0 mm.
  • the corrugated grooves 646 are represented by solid lines and the grooves 644 are represented by fine solid lines.
  • providing the projections 643 in the tube provided with the grooves 644 achieves a synergistic effect for the entire heat transfer tube due to the corrugated groove 646, the grooves 644, and the projections 643.
  • a corrugated heat transfer tube 65 employed in a sixth embodiment comprises a section 65a and a section 65b.
  • a corrugated heat transfer tube not provided with projections is used in the section 65b positioned in the vicinity of a water outlet 652; in the other section 65a, projections 653 each having a height of 1.0 mm are provided in the grooved tube provided with corrugated grooves 656 each having a depth of 0.5 mm and grooves 654 each having a depth of 0.2 mm.
  • the corrugated grooves 656 are represented by solid lines, and the grooves 654 are represented by fine solid lines.
  • a corrugated heat transfer tube 66 employed in a seventh embodiment comprises three sections: a section 66a, a section 66b, and a section 66c.
  • a grooved tube provided with corrugated grooves 666 each having a depth of 0.5 mm and grooves 664 each having a depth of 0.2 mm, in which projections 663 each having a height of 1.0 mm are provided, is employed;
  • a corrugated heat transfer tube provided with the corrugated grooves 666 each having a depth of 0.5 mm is employed;
  • the corrugated grooves 666 are represented by solid lines, and the grooves 664 are represented by fine solid lines.
  • a synergistic effect is achieved in that the projections 663, the grooves 664, and the corrugated grooves 666 improve heat transfer performance in the section where the Reynolds number is low, and the grooves 664 and the corrugated grooves 666 improve heat transfer performance in the section where the Reynolds number is high, thereby improving the performance of the entire heat exchanger.
  • scaling is suppressed by the corrugated grooves 666 in the section 66c positioned in the vicinity of the water outlet 662, where the water temperature is high.
  • a heat transfer tube 67 employed in an eighth embodiment comprises three sections: a section 67a, a section 67b, and a section 67c.
  • a corrugated tube provided with the corrugated grooves 666 each having a depth of 0.5 mm, in which projections 673 each having a height of 1.0 mm are provided, is employed;
  • a corrugated heat transfer tube provided with corrugated grooves 676 each having a depth of 0.5 mm is employed; and the grooved tube 67b provided with the corrugated grooves 676 each having a depth of 0.5 mm and grooves 674 each having a depth of 0.2 mm is employed between the section 67a and the section 67c.
  • the corrugated grooves 676 are represented by solid lines, and the grooves 674 are represented by fine solid lines.
  • a synergistic effect is achieved in that the corrugated grooves 676 and the projections 673 improve heat transfer performance in the section where the Reynolds number is low, and the corrugated grooves 676 and the grooves 674 improve heat transfer performance in the section where the Reynolds number is high, thereby improving the performance of the entire heat exchanger.
  • scaling is suppressed by the corrugated grooves 676 in the section 67c positioned in the vicinity of the water outlet 672, where the water temperature is high.
  • projections 683 are provided in a linear part 684, but projections are not provided in bent pares B1 - B7 (dotted area). Not providing projections on the inner surface of the bent parts B1 - B7 can avoid increasing the pressure loss in the tube, and can also avoid the occurrence of large deformations, breaks, and the like, during the bending work process.
  • Figure 19(a) is a plan view of a corrugated heat transfer tube 69 employed in a tenth embodiment
  • Figure 19(b) is a perspective view of the heat transfer tube 69.
  • projections 693 are provided in a linear part 694, but projections are not provided in a section 695 that intersects with a bent surface S1 in a bent part C - C.
  • a corrugated heat transfer tube 70 used in an eleventh embodiment projections are not used in a contact region between an outer surface 71 of the corrugated heat transfer tube and a refrigerant tube 72.
  • the contact between the refrigerant tube 72 and the heat transfer tube outer surface 71 degrades, creating a risk of decreasing the effect of the transfer of heat from the refrigerant tube 72. Therefore, providing projections 713 in the region where the refrigerant tube 72 is not wound around can prevent a reduction in the effect of transferring heat from the refrigerant tube 72.
  • a corrugated tube having corrugated grooves, which serves as a heat transfer tube is provided with projections.
  • a high-fin tube provided with projections may be employed as a heat transfer tube as shown in Figure 21(b) ; or a flower printed tube provided with projections maybe employed as a heat transfer tube as shown in Figure 21(c) .

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Fluid Heaters (AREA)
EP07792965A 2006-09-08 2007-08-24 Tube ondulé pour échangeur thermique destiné à une alimentation en eau chaude Withdrawn EP2071266A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CNA2006101130277A CN1924507A (zh) 2006-09-08 2006-09-08 用于热水器的螺旋槽换热管
PCT/JP2007/066436 WO2008029639A1 (fr) 2006-09-08 2007-08-24 tube ondulÉ pour Échangeur thermique destinÉ À une alimentation en eau chaude

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EP2071266A1 true EP2071266A1 (fr) 2009-06-17
EP2071266A4 EP2071266A4 (fr) 2013-01-23

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US (1) US20090250198A1 (fr)
EP (1) EP2071266A4 (fr)
JP (1) JP4768029B2 (fr)
KR (1) KR20090055604A (fr)
CN (1) CN1924507A (fr)
AU (1) AU2007292663B2 (fr)
WO (1) WO2008029639A1 (fr)

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EP2071266A4 (fr) 2013-01-23
CN1924507A (zh) 2007-03-07
AU2007292663A1 (en) 2008-03-13
WO2008029639A1 (fr) 2008-03-13
JP4768029B2 (ja) 2011-09-07
KR20090055604A (ko) 2009-06-02
AU2007292663B2 (en) 2010-08-12
JPWO2008029639A1 (ja) 2010-01-21

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