WO2000016029A1 - Echangeur de chaleur et systeme de conditionnement d'air refrigerant - Google Patents

Echangeur de chaleur et systeme de conditionnement d'air refrigerant Download PDF

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Publication number
WO2000016029A1
WO2000016029A1 PCT/JP1998/004155 JP9804155W WO0016029A1 WO 2000016029 A1 WO2000016029 A1 WO 2000016029A1 JP 9804155 W JP9804155 W JP 9804155W WO 0016029 A1 WO0016029 A1 WO 0016029A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat transfer
transfer surface
heat
plate
heat exchanger
Prior art date
Application number
PCT/JP1998/004155
Other languages
English (en)
Japanese (ja)
Inventor
Hitoshi Matsushima
Mari Uchida
Atushi Kubota
Mitsugu Aoyama
Original Assignee
Hitachi, Ltd.
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Hitachi, Ltd. filed Critical Hitachi, Ltd.
Priority to JP2000570520A priority Critical patent/JP3747780B2/ja
Priority to PCT/JP1998/004155 priority patent/WO2000016029A1/fr
Publication of WO2000016029A1 publication Critical patent/WO2000016029A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/044—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being pontual, e.g. dimples
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media

Definitions

  • the present invention relates to a heat exchanger and a refrigeration / air-conditioning system, and is particularly suitable for a chiller unit using a plate-type heat exchanger.
  • a plurality of relative beads protruding inward from the heat exchange medium flow path composed of the two molding plates is formed.
  • An example of the installation is the one described in Japanese Patent Laid-Open Publication No. 4-32697.
  • the distance to the downstream side should be increased to increase the distance. Group is arranged.
  • JP-A-4-132697 a bead group is used. Although the pressure loss is reduced by thinning out the flow, the turbulence in the flow path is reduced and the heat transfer performance is reduced.
  • An object of the present invention is to make a difference.
  • An object of the present invention is to provide a heat exchanger and a refrigeration / air-conditioning system that have good heat transfer performance and low pressure loss.
  • the purpose of the present invention is to reduce the amount of refrigerant used and reduce the risk of destruction of the ozone layer by improving the performance and the size of the heat exchanger.
  • the purpose of the present invention is to provide a heat exchanger and a refrigeration / air-conditioning system that address environmental issues such as preventing global warming.
  • the purpose of the present invention is to improve the performance of the ripening exchanger with a small amount of refrigerant, to increase the tightness of the heat exchanger, and to use a natural refrigerant.
  • An object of the present invention is to provide a heat exchanger and a refrigeration / air-conditioning system that have high efficiency and that are highly safe against the flammability and toxicity of natural refrigerants.
  • the present invention is to solve at least one of the above-mentioned problems.
  • the present invention relates to a heat exchanger in which a plurality of plates having an inlet and an outlet for a heat exchange fluid are stacked, and the plate surface is provided on the plate.
  • a seal portion provided with the inflow port and the outflow port communicating with an inner portion, and a heat exchange fluid flow path formed in the seal portion.
  • a heat transfer surface element formed in a mountain or valley shape in the thickness direction of the plate, and a fine fin formed on the surface of the heat transfer surface element and having concave and convex portions. It is provided.
  • a heat transfer surface element protruding in a mountain or valley shape is arranged in the seal portion of the plate, and a plurality of the heat transfer surface elements are laminated to form a flow path of a heat exchange fluid.
  • the exchange fluid flows while repeating meandering, maintains appropriate fluid mixing, improves heat transfer performance, and can be made much more compact than those using conventional pipes.
  • the heat transfer surface elements protrude and extend in the thickness direction of the plate, the bending rigidity of the plate is increased, and the upper and lower portions of each plate are increased. Since it is possible to have a contact point between each other, the pressure resistance as a heat exchanger can be increased. In addition, since concave and convex fine fins are formed on the surface of the heat transfer surface element, turbulent frictional resistance to the flow of the heat exchange fluid is reduced, and pressure loss is reduced. It can be reduced. Therefore, the heat exchanger can be made compact, the heat transfer performance can be improved, and the power and pressure loss can be reduced.
  • the present invention is based on the fact that plates are stacked in a heat exchanger having an inlet and an outlet for heat exchange fluid and using a plate.
  • a heat transfer surface element having a height of 2 to 3 mm, and a heat transfer surface element, which is arranged on the plate surface so that a heat exchange fluid flow path is formed.
  • the surface has irregularities of 0.1 to 1.0 mm.
  • the height of the heat transfer surface element is 2 to 3 mm, and the flow path of the heat exchange fluid is formed between a plurality of plates by the arrangement of the heat transfer surface element. Therefore, it becomes a thin and compact heat exchanger. Furthermore, the fine fins having irregularities of 0.1 to 1.0 mm reduce turbulent frictional resistance to the flow of the heat exchange fluid in the flow path. Therefore, the pressure loss is reduced, and a high heat transfer coefficient can be obtained. Further, in the present invention, as described above, the heat transfer surface elements are rectangular in shape when viewed from the top surface, are arranged in a net shape, and are arranged from the bottom surface of the plate to the upper end of the heat transfer surface elements. It has a slope that slopes toward the part, the fine fins are formed in the slope, and the height of the concave and convex is the height of the heat transfer surface element. It is smaller.
  • the upper end of one heat transfer surface element and the bottom surface of the other of the plurality of plates are stacked so as to face each other.
  • the heat transfer surface element has a mountain shape with a flat top.
  • some of the heat transfer surface elements have a triangular shape when viewed from the top, and one side thereof is substantially perpendicular to the direction of flow of the heat exchange fluid. It is something.
  • the present invention relates to a heat exchanger in which a plurality of plates each having an inlet and an outlet for a heat exchange fluid are stacked, and the plate is bent in a corrugated manner.
  • the heat exchange fluid flow path is formed between the upper and lower plates so that the bending direction is perpendicular to the bending direction, and a heat exchange fluid flow path is formed between the upper and lower plates. It has a fine fin on which concaves and convexes smaller than the size are formed.
  • the flow path formed between the plates is meandering, the mixing of the heat exchange fluid is promoted, and the heat transfer performance is improved. Since the turbulent frictional resistance to the flow of the heat exchange fluid is reduced by the fine fins, the pressure loss is reduced. Plates can also be easily and inexpensively produced by press processing.
  • the present invention relates to a refrigeration and air-conditioning system having a compressor, a heat exchanger, and an expansion valve, in which a plurality of plates are stacked to exchange heat. It is equipped with a heat exchanger having fine fins with concave and convex smaller than the size of the fluid flow path.
  • the fine fins improve the heat transfer performance of the heat exchanger and reduce the pressure loss, making it easier to reduce the size of the refrigeration and air-conditioning system and increasing the amount of refrigerant used. And to be suitable for addressing environmental issues such as preventing global warming.
  • the present invention has a compressor, a heat exchanger, an expansion valve, and a heat transfer surface formed in a mountain or valley shape in a refrigeration and air conditioning system through which a refrigerant flows.
  • the flow path of the refrigerant was formed by laminating a plurality of plates each having a fine fin formed in a concave and convex shape on the surface of the heat transfer surface. It is equipped with a heat exchanger.
  • the performance of the heat exchanger can be improved, so that even if a natural refrigerant is used, the efficiency is good, and the amount of the refrigerant can be reduced, so that the flammability of the natural refrigerant can be reduced.
  • Safety can be increased with respect to sex and toxicity.
  • non-azeotropic mixing is used as the refrigerant, and the flow of the refrigerant is opposed to the flow path of the adjacent plate. This is what we have done.
  • the present invention has a compressor, a heat exchanger for exchanging heat between water and a refrigerant, an expansion valve, a pump, a water tank, and a fan convection unit installed indoors.
  • the water side of the heat exchanger is connected to the water tank, and the water in the water tank is guided to the fancoin unit by the pump.
  • the heat exchanger is laminated by a plurality of plates, and is provided on the plate surface, and the inflow port and the outflow port communicate with each other. And a seal or valley formed in the seal in the thickness direction of the plate. This is provided with a protruding heat transfer surface element and fine fins formed on the surface of the heat transfer surface element and having irregularities.
  • the heat transfer performance of the heat exchanger is improved and pressure loss is reduced, so that the amount of refrigerant used is reduced and the heat exchange of the heat exchanger is performed by the seal portion. Since the degree of closure is increased and the refrigerant is not transported indoors, the use of natural refrigerants enhances the safety of flammability and toxicity. be able to.
  • the refrigerant is an HC refrigerant.
  • FIG. 1 is a plan view of a plate used in a heat exchanger according to an embodiment of the present invention
  • FIG. 2 is a state in which the plate 1 is alternately turned upside down and stacked.
  • Fig. 3 and Fig. 4 are cross-sectional views in which main parts are enlarged
  • Fig. 5 is a perspective view in which heat transfer surface elements are enlarged
  • Fig. 6 is a cross-sectional view in which main parts are enlarged.
  • FIG. 7 is a plan view of a plate according to another embodiment
  • FIG. 8 is a perspective view of a heat transfer surface element according to another embodiment
  • FIG. 9 is a plan view of still another embodiment.
  • FIG. 10 is a perspective view of a heat transfer surface element according to still another embodiment.
  • FIG. 10 is a perspective view of a heat transfer surface element according to still another embodiment.
  • FIG. 11 is a plan view showing an arrangement of heat transfer surface elements.
  • 2 is a cross-sectional view of a heat exchanger according to another embodiment
  • FIG. 13 is a plan view showing an arrangement of heat transfer surface elements according to still another embodiment
  • FIG. Sa Fig. 15 is a plan view showing an arrangement of heat transfer surface elements according to another embodiment
  • Fig. 15 is a plan view of a plate according to another embodiment
  • Fig. 16 is a plan view of the plate according to another embodiment.
  • FIG. 17 is a cross-sectional view of a heat exchanger according to another embodiment.
  • FIG. 17 is a cross-sectional view of a heat exchanger according to another embodiment.
  • FIG. 18 is a cross-sectional view of FIG.
  • FIG. 25 is a perspective view and a view of a heat exchanger according to still another embodiment.
  • FIG. 26 is a sectional view of the heat exchanger according to the embodiment of FIG. 25, FIG. 27 is a plan view of a plate according to still another embodiment, and FIG. FIG. 29 is a cross-sectional view of FIG. 28, FIG. 30 is a partial perspective view of a heat exchanger according to another embodiment, and FIG. 30 is a partial perspective view of a heat exchanger according to another embodiment.
  • FIG. 31 is a perspective view
  • FIG. 31 or FIG. 33 is a partial plan view of a plate according to still another embodiment
  • FIG. 34 is a partial plan view of still another embodiment. Partial cross-sectional view of heat exchanger
  • FIG. 35 is a schematic diagram of FIG. 34
  • FIG. 36 is a block diagram of a refrigeration / air-conditioning system according to still another embodiment.
  • a heat exchanger is formed by laminating a plurality of plates with heat exchangers, forming flow paths between the plates, and alternately flowing fluids with different temperatures through these flow paths.
  • FIG. 1 is a plan view of a plate 1 used in the heat exchanger of one embodiment
  • FIG. 5 is an enlarged perspective view of a heat transfer surface element 3.
  • FIG. 2 is a plan view showing a state in which the plates 1 are alternately turned upside down and stacked
  • FIGS. 3, 4, and 6 are cross-sectional views in which main parts thereof are enlarged.
  • Plate 1 can be made by pressing a thin metal plate.
  • Plate 1 has four openings 2a, 2b, 2c, and 2d. However, only the inner openings 2a and 2b serve as an inlet and an outlet of the heat exchange fluid, respectively, and communicate with the inner portion of the seal portion 4.
  • the upper and lower two opening portions 2 c and 2 d are separated by a sinuous portion 4.
  • the heat transfer surface elements 3 protrude in the thickness direction of the plate 1 in the form of peaks or valleys, have a square shape, are arranged in a net shape, or are arranged in a large number in a staggered manner. In the meantime, the flow path 5 is formed in a shaded manner. As shown in Fig.
  • the heat transfer surface element 3 has a shape that slightly travels in the vertical direction with respect to the plate 1 surface, and has a flat surface with the plate 1 bottom surface. There is a slope between the upper end 6 and the upper end 6 that slopes from the bottom to the upper end. And, in the slope portion, there are provided fine fins 7 in which a number of fine wavy concaves and convexes sufficiently smaller than the height of the heat transfer surface element 3 are formed. It is.
  • the height and pitch of the concaves and convexes of the fine fins 7 are, for example, such that the height of the heat transfer surface element 3 is about 2 to 3 mm and 0.1 to 1.0 mm, preferably 0.1 to 1.0 mm. A value around 0.5 mm or less is good.
  • the heat exchanger according to the present embodiment When the heat exchanger according to the present embodiment is used, for example, as a water-refrigerant heat exchanger for a chillet, the heat exchange performance and the influence of gravity are considered. It is effective to have a completely counter-current flow with the following flow direction. That is, in the case of an evaporator, the refrigerant flows in from the lower opening 2a, flows between the heat transfer surface elements 3 on the plate 1, and then flows into the upper opening 2b. Water flows from the upper opening 2 d, flows between the heat transfer surface elements 3 on the adjacent plate 1, and then flows to the lower opening 2 c. Spill.
  • the refrigerant flows in from the upper opening 2b, and After flowing between the heat transfer surface elements 3 on the plate 1, the water flows out from the lower opening 2 a, and water flows in from the lower opening 2 c, and the water flows into the next opening. After flowing between the heat transfer surface elements 3 on the plate 1, the gas is allowed to flow out from the upper opening 2 d.
  • Making the flow completely countercurrent is particularly effective in improving the efficiency of the refrigeration cycle when a non-azeotropic refrigerant such as R407C is used as the refrigerant. is there.
  • the fluid used for the refrigeration cycle can be obtained.
  • the cycle can be simplified when one of the heat exchangers for warm and cold is a heat exchanger for refrigerant-air.
  • the fluid between the plates 1 flows on the heat transfer surface element 3 without being greatly restricted.
  • the fine fins 7 provided on the heat transfer surface element 3 reduce the turbulent frictional resistance by interfering with the turbulent striped structure. In particular, it is effective in reducing pressure loss in a single-layer flow. Therefore, the pressure loss at the three heat transfer surface elements can be significantly reduced as compared with the conventional one.
  • the fluid flowing between the plates 1 collides with the heat transfer surface element 3 and then the fine fins formed in the slope portion It flows smoothly along 7.
  • the fine fins 7 perform the same function as micro fins in a heat transfer tube with a groove inside the tube, and can obtain a high heat transfer coefficient.
  • the plate 1 is used as an evaporating surface
  • the refrigerant in the two-phase flow state impinges on the heat transfer surface element 3 and then becomes finer due to the effect of the capillary effect.
  • the heat transfer surface element 3 spreads over substantially the entire area along the heat transfer surface element 7, and the entire heat transfer surface element 3 becomes wet.
  • the refrigerant in a two-phase flow state collides with the heat transfer surface element 3 and then flows along the fine fins 7, but the liquid is In addition to the large inertia of the fins, the effect of the surface tension pulling the liquid to the gap side of the fine fins 7 and the same surface tension creates the liquid at the upper end 6
  • the thin portion of the liquid film is formed at the tip of the fine fin 7 due to the synergistic effect with the effect of stretching the cavity.
  • the refrigerant or water flows through the upper and lower surfaces of the heat transfer surface element 3, but as shown in FIG. In this case also, the fluid collides with the upper surface or the lower surface of the fine fin 7, so that a very high heat transfer coefficient is obtained in this portion, and the heat exchange is performed very efficiently.
  • the three-dimensional turbulence generated when flowing between the heat transfer surface elements 3 is effective not only on the water side but also on the refrigerant side, and in particular, the non-uniformity represented by R407C
  • An azeotropic refrigerant mixture can diffuse gas components, which are more likely to be present near the heat transfer surface and less likely to undergo a phase change, to other locations. You.
  • the three-dimensional disorder can prevent the scale and the like from adhering to the surface of the plate 1.
  • the flow pipe flowing on the plate 1 is formed while the flow path 5 formed between the heat transfer surface elements 3 is repeatedly branched and joined.
  • the flow balance between the heat transfer surface elements 3 has been improved, and the Due to the pressure recovery effect due to the small gap, it is possible to obtain a very good flow distribution.
  • the variation in the heat transfer performance between the heat transfer surface elements 3 on the plate 1 is reduced, which is advantageous for the heat exchanger. is there.
  • the shape of the heat transfer surface element 3 is a square shape or a square rhombus shape when viewed from the top, but the present invention is not limited to this. You may use something like a honeycomb pattern in which regular hexagons are arranged.
  • the shape of the heat transfer surface element 3 in the present embodiment is the same as that of the embodiment of FIGS. 1 to 6 except that the upper end 6 of the heat transfer surface element 3 is located downstream. It is. By holding the upper end portion 6 on the downstream side as shown in the figure, almost all of the slope of the heat transfer surface element 3 faces forward with respect to the flow.
  • the fine fins 7 provided on the hot surface element 3 function more effectively, and are very effective when the flow direction of the heat exchange fluid is constant.
  • FIGS. 8 and 9 show still another embodiment of the heat transfer surface element 3 of the present invention.
  • the heat transfer surface element 3 has a triangular shape when viewed from the upper surface and an isosceles triangular shape with a pointed tip, and one side thereof is substantially perpendicular to the direction in which the flow of the heat exchange fluid flows.
  • the heat exchange fluid flows more smoothly than the one in FIG. 7, and it is effective in further reducing the pressure loss when the heat exchange fluid flows over the heat transfer surface element 3. You.
  • FIG. 10 shows another example of the heat transfer surface element 3 of the present invention. This is an embodiment.
  • the heat transfer surface element 3 has a crescent shape when viewed from above. Since the fluid flowing between the plates 1 is not greatly restricted, the pressure loss at the three heat transfer surface elements is limited to the hermetic type described in the prior art. It is greatly reduced compared to the rate.
  • the heat transfer surface element 3 may be an array pattern as shown in FIGS. 11, 13, and 14.
  • the arrangement pattern shown in Fig. 11 is obtained by disposing the heat transfer surface elements 3 in the same direction, and is effective in maintaining uniform flow distribution.
  • the direction of the heat transfer surface element 3 is reversed for each row, and the mixing of fluids is increased and the heat transfer performance is improved.
  • Figure 14 shows the array. In the turn, the direction of the heat transfer surface element 3 is horizontal and reversed in each row, and the fluid flows through a force that does not repeat meandering. Pressure loss can be suppressed to a low level while maintaining mixing.
  • FIG. 15 to FIG. 17 show another embodiment of the heat exchanger of the present invention.
  • the upper end 6 of the heat transfer surface element 3 is provided at two places at both ends of the heat transfer surface element 3, and is formed by a number of fine wavy irregularities so as to be sandwiched between the two upper ends 6.
  • the fine fins 7 to be formed are provided.
  • the effect of the fine fins 7, the effect of three-dimensional turbulence generated when flowing between the heat transfer surface elements 3, and the flow path while repeating branching and joining by the flow path 5 The effect of improving the flow balance between the five is almost the same as in the above embodiment.
  • FIG. 18 shows still another embodiment of the heat exchanger of the present invention.
  • the shape of the heat transfer surface element 3 is the same as that of FIG. 15 or FIG. 17 except for both ends of the plate 1.
  • the upper end 6 of the heat transfer surface element 3 is provided at two places at both ends and at the center, a total of three places, and the flow resistance at this part is relatively large. It's getting better Therefore, there is a great effect on the improvement of flow distribution.
  • the flow rate distribution in the plate 1 can be kept uniform without significantly increasing the overall pressure loss of the plate 1.
  • FIG. 19 shows still another embodiment of the heat exchanger of the present invention.
  • the shape of the heat transfer surface element 3 is such that the upper end portion 6 of the heat transfer surface element 3 is provided at one central portion of the heat transfer surface element 3 and has many fine wavy irregularities on both sides.
  • the fine fins 7 to be formed are provided.
  • the flow resistance when the fluid flows between the heat transfer surface elements 3 on the plate 1 is relatively small compared to the one already described, and the flow velocity may differ.
  • the guide 8 is provided around the entrance / exit opening 2, the flow distribution in the plate 1 can be kept uniform.
  • FIG. 20 shows still another embodiment of the heat exchanger of the present invention.
  • a large number of fine fins 7 each having an upper end portion 6 are provided on the heat transfer surface element 3, and a secondary flow path 9 is formed between the fine fins 7.
  • the flow resistance when the fluid flows between the heat transfer surface elements 3 on the plate 1 is relatively large as compared with the above-described embodiment, and the flow distribution in the plate 1 is further increased. It can be kept good.
  • FIG. 21 shows a heat transfer surface element 3 in which the height of the fine fins 7 is reduced in the same manner as in FIG. 20 but at a suitable interval near the center of the plate 1. It is a sign. This makes it possible to reduce the overall pressure loss of the plate 1 while keeping the flow distribution in the plate 1 uniform.
  • the plate 1 is made by pressing a thin metal plate having high durability and high corrosion resistance such as stainless steel.
  • the present invention is not limited to this, and the plate 1 is formed by cutting or other processing methods. It may be made by Also, during press processing, heat is transferred to a part coated with a soft metal such as aluminum or copper on a stainless steel plate, for example. When the surface element 3 is formed, it becomes easy to form the fine fin 7 having a complicated shape.
  • FIG. 22 shows an embodiment in which the plate 1 is made by cutting. After all the heat transfer surface elements 3 have been formed to the same height as the upper end 6 for the first time, they are lowered by cutting and at the same time, fine fins with many fine concaves and convexes The molding of 7 is performed. In order to obtain the compressive strength, elements that do not lower the height (with the upper end 6) are provided at appropriate intervals on the plate 1. For this reason, the overall pressure loss of the plate 1 can be reduced while maintaining an appropriate heat transfer performance and the flow distribution in the plate 1.
  • FIG. 23 also shows another embodiment in which the plate 1 is made by cutting.
  • the direction and shape of the fine fins 7 and the arrangement notch force S of the heat transfer surface element 3 having the same are different from those in FIG.
  • Figure 24 shows the heat transfer surface element 3 with chamfers 10 at both ends. Since the chamfering 10 can prevent the occurrence of separation flow at both ends of the heat transfer surface element 3, it is effective in reducing pressure loss and improving the stability of flow distribution. You.
  • FIGS. 25 to 29 show an embodiment in which the plate 1 is formed by press working.
  • Fig. 25 shows a plate formed by stacking two types of plates 1 each having a corrugated heat transfer surface made by pressing. G heat exchanger.
  • the pressure resistance can be increased by the large number of contact surfaces formed between the plate 1 and the plate ⁇ .
  • the expanded heat transfer surface effect at Plate ⁇ is remarkable.
  • Figure 26 As shown, the fluid flowing between the plates 1, mainly flows between the plates ⁇ , but is formed at a more appropriate spacing than the plates 1. Repeats meandering for the existence of the space. And, due to the turbulence generated by the meandering, the mixing of the fluid is promoted and the heat transfer performance is improved. In addition, the flow of fluid flowing between the plates 1 while the fluid flowing between the plates is repeatedly delivered to the space formed by the plate 1 Is improved. In addition, since the fluid flowing between the plates 1 and 1 'is rarely throttled, the pressure loss is very small.
  • the embodiment shown in Fig. 27 or Fig. 29 is a plate type heat exchange type in which plates 1 made by press working are alternately turned upside down and stacked. Vessel. A plurality of fine fins 7 formed by a number of fine wavy irregularities are provided between the upper end portions 6 parallel to each other in the flow direction, and a plurality of regions are provided. Is provided with a protrusion 11. Therefore, the protrusion 11 promotes the mixing of the fluid, and the heat transfer performance is improved.
  • the fluid flowing on the plate 1 is hardly throttled, so that the pressure loss is extremely small. Small.
  • a guide 8 is provided around the inlet / outlet opening 2. Therefore, it is easy to keep the flow distribution in the plate 1 uniform.
  • Fig. 30 shows the upper end 6 and the fine fin 7 of Fig. 27 or Fig. 29, which are formed by meandering. It can promote mixing of fluids.
  • the flow rate distribution near the opening 2 of the plate 1 is further improved.
  • Guide 8 in Fig. 31 distributes the flow rate by repeating branching and merging.
  • the angle ⁇ of the guide 8 becomes smaller as it is closer to the opening 2. This makes it possible to easily perform a uniform two-phase branch on the upstream side and a uniform flow branch on the downstream side, particularly at the opening 2 on the inlet side.
  • FIG. 34 is an enlarged cross-sectional view of the main part near the opening 2 when the plates 1 are alternately turned upside down and stacked.
  • Fig. 35 schematically shows Fig. 34 with respect to the refrigerant inlet 13 of the evaporator, and the refrigerant flows into the two-phase flow at the refrigerant inlet 13 of the evaporator. Then, the liquid flows in, and a relatively large amount of liquid accumulates on the lower side. In this case, depending on the operating condition of the plate type heat exchanger, the liquid level may be changed between the inlet 13 side and the opposite side.
  • the structure shown in Fig. 32 or Fig. 33 is improved in view of the above points.
  • a partition plate 12 also serving as an upper end 6 is provided at the opening 2 so as to face the inside of the plate 1, and the refrigerant flowing from the inlet 13 is provided. Since only the lower side of the opening 2 enters the heat transfer section of the plate 1 from the cap, it becomes easy to supply the liquid evenly to all the plates 1.
  • Fig. 33 differs from Fig. 32 in that the shape of the opening 2 is crescent-shaped, and the refrigerant flowing from the opening 2 is very smooth. — Since the heat enters the heat transfer section of the plate 1, it is easy to supply the liquid evenly to all the plates 1, and the pressure loss at the opening 2 can be reduced.
  • the partition plate 12 is Although the upper end 6 is also used, this configuration can improve the pressure resistance in the vicinity of the opening 2.
  • the plate type heat exchanger of the present invention has good heat transfer performance, is compact and has low pressure loss, so that the amount of refrigerant to be used can be extremely reduced.
  • it is advantageous for preventing global warming when using an alternative refrigerant such as HFC refrigerant and preventing danger when using a natural refrigerant such as HC refrigerant and ammonia.
  • a heat transfer unit having a plurality of plate-type heat transfer sections composed of two plates 1 is applied to an air conditioner for ice storage, a heat storage tank can be provided. Compaction-shortens the ice making time or improves the ice filling rate, which is also advantageous for peak power shift and power leveling.
  • FIG. 36 shows an embodiment of a refrigeration / air-conditioning system according to the present invention.
  • the basic refrigeration cycle is composed of heat exchangers 20a and 20b for water and refrigerant, a compressor 21 and an expansion valve 22a, and the heat exchangers 20a and 2Ob A plurality of plates are stacked, and a fine fin 7 having concaves and convexes smaller than the size of the flow path of the heat exchange fluid is provided.
  • the fine fins 7 improve the heat transfer performance of the heat exchanger and reduce the pressure loss, so that the size of the refrigeration / air-conditioning system can be easily reduced. Reducing the amount of refrigerant to be used can address environmental issues such as preventing global warming.
  • the water side of the heat exchangers 20a and 20b is connected to the high and low temperature water tanks 27a and 27b, and the pumps 23a and 23b Drive Be moved.
  • a noise circuit having an expansion valve 22b and an ice making unit 24 will be provided.
  • the ice making unit 24 also has a fine fin 7 in which a plurality of plates are stacked and irregularities smaller than the size of the flow path of the heat exchange fluid are provided. It is a plate-type heat transfer unit that uses a heat exchanger.
  • the water in the water tank 27a or the water tank 27b is discharged by the pump 23c after either one is selected by the simultaneous switching of the two three-way valves 28. After being driven, it is guided to the fan connole unit 29, and after exchanging heat with air, returns to the original water tank 27a or 27b.
  • the water in the water tank 27a or the water tank 27b exchanges heat with the water-to-water heat exchangers 25a and 25b to supply hot or cold water.
  • the fans 26a and 26b in the water tanks 27a and 27b operate when the water temperature in the water tanks 27a and 27b rises or falls abnormally. You.
  • the expansion valve 22b When performing cooling operation with the fan coil unit 29, usually, the expansion valve 22b is kept closed and the cold water is produced by the basic refrigeration cycle. However, if there is room for cooling capacity at night, etc., the expansion valve 22b is squeezed and opened slightly to prepare cold water using the basic refrigeration cycle and ice making unit. Simultaneously produce ice by using the method described in step 24. In order to prevent all the water in the water tank 27b from freezing, the pump 23b should always be operated regardless of the operation status of the basic refrigeration cycle. When the ice is sufficiently prepared, the basic refrigeration cycle is suspended, and cold water is supplied from the ice making unit 24 side. As a result, the compressor 21 can always be operated near the most efficient rated point, and the energy efficiency is improved.
  • the refrigerant cannot enter the indoor space, so that HC refrigerant, ammonia, and other flammable fuels can be used. It is possible to prevent danger when using natural refrigerants, which are concerned about their properties and toxicity.
  • a heat transfer surface element protruding in a mountain or valley shape is arranged in a seal portion of a plate, and a plurality of heat transfer surface elements are stacked to form a flow path of a heat exchange fluid.
  • the heat exchange fluid flows while repeating meandering, maintaining an appropriate fluid mixture and improving heat transfer performance, and having a compact heat transfer performance and good pressure loss. It is possible to obtain a small number of heat exchangers and refrigeration and air conditioning systems.
  • concave and convex fine fins are formed on the surface of the heat transfer surface element, the turbulent frictional resistance to the flow of the heat exchange fluid is reduced, and the pressure loss is further reduced.
  • the height of the heat transfer surface element is 2 to 3 mm, and the flow path of the heat exchange fluid between the plurality of plates depends on the arrangement of the heat transfer surface element.
  • the fine fins that are formed and have concaves and convexes of 0.1 to 1.0 mm reduce the turbulent frictional resistance to the flow of the heat exchange fluid in the flow path. Therefore, it is possible to obtain a compact heat exchanger and refrigeration / air-conditioning system with a high heat transfer coefficient.
  • the plates bent in a corrugated manner are stacked one on top of the other so that the bending direction is orthogonal, and the upper and lower plates are stacked.
  • a flow path of the heat exchange fluid is formed between the plates, and the fine fins have irregularities smaller than the thickness in the thickness direction of the platen. Therefore, the flow paths meander, the mixing of the heat exchange fluid is promoted, the turbulent frictional resistance is reduced by the fine fins, the pressure loss is reduced, and the plate is pressed. It can be created by IIe. Therefore, it is possible to obtain a compact heat exchanger and a refrigeration air-conditioning system with a small pressure loss and a low price.
  • a fine fin in which a plurality of plates are stacked and irregularities smaller than the size of the flow path of the heat exchange fluid are provided. Therefore, the fine fins improve the heat transfer performance of the heat exchanger and reduce the pressure loss, so that the size of the refrigeration and air-conditioning system can be easily reduced and used. By reducing the amount of refrigerant used, it is possible to obtain a heat exchanger and a refrigeration / air-conditioning system that are suitable for environmental problems such as preventing global warming.
  • a plate having a heat transfer surface formed in a mountain or valley shape and a fine fin formed in a concave and convex shape on the surface of the heat transfer surface is provided. Since a heat exchanger with a refrigerant flow path formed by stacking multiple heat exchangers is provided, the performance of the heat exchanger can be improved, and natural refrigerants can be used. In addition, it is possible to obtain a heat exchanger and a refrigeration / air-conditioning system with improved efficiency, reduced amount of refrigerant, and improved safety with respect to the flammability and toxicity of the refrigerant.
  • the water side of the heat exchanger is connected to the water tank, and the water in the water tank is guided to the fan-coin unit by the pump.
  • the heat exchanger is laminated by a plurality of plates, and a seal portion in which an inlet and an outlet are communicated to the inside, and a thickness of the plate. Heat transfer surface protruding in a mountain or valley direction

Abstract

L'invention concerne un échangeur de chaleur compact capable d'excellentes performances en matière de transfert thermique pour une faible perte de pression. Plusieurs plaques (1) stratifiées sont munies chacune d'un orifice d'amenée et d'un orifice d'évacuation. Chaque plaque (1) comprend, sur une de ses surfaces, une partie étanche (4), des passages d'écoulement (5) du fluide d'échange thermique formés dans la partie étanche (4), des éléments superficiels de transfert thermique (3) ayant une forme de montagne ou de vallée saillante ou en retrait dans le sens de l'épaisseur de la plaque (1), et des nervures fines (7) présentant des creux et des aspérités et formées sur la surface des éléments superficiels de transfert thermique. L'invention concerne en outre un système de conditionnement d'air réfrigérant.
PCT/JP1998/004155 1998-09-16 1998-09-16 Echangeur de chaleur et systeme de conditionnement d'air refrigerant WO2000016029A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2000570520A JP3747780B2 (ja) 1998-09-16 1998-09-16 熱交換器
PCT/JP1998/004155 WO2000016029A1 (fr) 1998-09-16 1998-09-16 Echangeur de chaleur et systeme de conditionnement d'air refrigerant

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP1998/004155 WO2000016029A1 (fr) 1998-09-16 1998-09-16 Echangeur de chaleur et systeme de conditionnement d'air refrigerant

Publications (1)

Publication Number Publication Date
WO2000016029A1 true WO2000016029A1 (fr) 2000-03-23

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WO (1) WO2000016029A1 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2831654A1 (fr) * 2001-10-31 2003-05-02 Valeo Climatisation Tubes d'echangeur thermique a plaques optimisees
EP1500895A3 (fr) * 2003-07-22 2005-04-06 Modine Manufacturing Company Conduit pour échangeur de chaleur
US6926075B2 (en) 2002-06-24 2005-08-09 Hitachi Air Conditioning Systems Co., Ltd. Plate type heat exchanger
US7383687B2 (en) 2002-10-31 2008-06-10 Sharp Kabushiki Kaisha Regenerator method for manufacturing regenerator, system for manufacturing regenerator and stirling refrigerating machine
JP2009210235A (ja) * 2008-03-06 2009-09-17 Panasonic Corp 熱交換器
JP2014040963A (ja) * 2012-08-22 2014-03-06 Daikin Ind Ltd 水熱交換器
RU2529288C1 (ru) * 2013-06-27 2014-09-27 Государственный научный центр Российской Федерации-федеральное государственное унитарное предприятие "Исследовательский Центр имени М.В. Келдыша" Пакет пластин теплообменного аппарата
JP2015528890A (ja) * 2012-07-27 2015-10-01 ゼネラル・エレクトリック・カンパニイ 空気冷却式のエンジン表面冷却器
EP3023727A1 (fr) * 2014-11-24 2016-05-25 Taiwan SRP Heat Exchanger Inc. Plaque de guidage de fluide et échangeur de plaque associé

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012105144B4 (de) * 2012-06-14 2021-12-02 Gea Wtt Gmbh Plattenwärmetauscher in asymmetrischer Ausführung

Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS53137460A (en) * 1977-05-07 1978-11-30 Howa Mach Ltd Parting plate for heat exchanger
JPS5495062U (fr) * 1977-12-19 1979-07-05
JPS5634396A (en) * 1979-08-28 1981-04-06 Hitachi Ltd Two tank type washing machine
JPS5649293U (fr) * 1979-09-25 1981-05-01
JPS593268Y2 (ja) * 1978-01-17 1984-01-28 川崎重工業株式会社 熱交換器
JPS61107056A (ja) * 1984-10-31 1986-05-24 三洋電機株式会社 ヒ−トポンプ式給湯装置
JPS63213761A (ja) * 1987-03-02 1988-09-06 三井造船株式会社 冷暖房装置
JPS6335263Y2 (fr) * 1983-07-29 1988-09-19
JPH04139388A (ja) * 1990-09-29 1992-05-13 Hisaka Works Ltd プレート式熱交換器
JPH0666487A (ja) * 1992-08-13 1994-03-08 Showa Alum Corp 積層型熱交換器
JPH07269964A (ja) * 1994-03-30 1995-10-20 Toshiba Corp 空気調和装置
JPH08296909A (ja) * 1995-04-24 1996-11-12 Matsushita Refrig Co Ltd 冷凍装置
JP2577156B2 (ja) * 1992-02-20 1997-01-29 新日本製鐵株式会社 プレート型熱交換器を用いた製氷方法
JPH10132476A (ja) * 1996-10-28 1998-05-22 Daikin Ind Ltd プレート式熱交換器

Patent Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS53137460A (en) * 1977-05-07 1978-11-30 Howa Mach Ltd Parting plate for heat exchanger
JPS5495062U (fr) * 1977-12-19 1979-07-05
JPS593268Y2 (ja) * 1978-01-17 1984-01-28 川崎重工業株式会社 熱交換器
JPS5634396A (en) * 1979-08-28 1981-04-06 Hitachi Ltd Two tank type washing machine
JPS5649293U (fr) * 1979-09-25 1981-05-01
JPS6335263Y2 (fr) * 1983-07-29 1988-09-19
JPS61107056A (ja) * 1984-10-31 1986-05-24 三洋電機株式会社 ヒ−トポンプ式給湯装置
JPS63213761A (ja) * 1987-03-02 1988-09-06 三井造船株式会社 冷暖房装置
JPH04139388A (ja) * 1990-09-29 1992-05-13 Hisaka Works Ltd プレート式熱交換器
JP2577156B2 (ja) * 1992-02-20 1997-01-29 新日本製鐵株式会社 プレート型熱交換器を用いた製氷方法
JPH0666487A (ja) * 1992-08-13 1994-03-08 Showa Alum Corp 積層型熱交換器
JPH07269964A (ja) * 1994-03-30 1995-10-20 Toshiba Corp 空気調和装置
JPH08296909A (ja) * 1995-04-24 1996-11-12 Matsushita Refrig Co Ltd 冷凍装置
JPH10132476A (ja) * 1996-10-28 1998-05-22 Daikin Ind Ltd プレート式熱交換器

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2831654A1 (fr) * 2001-10-31 2003-05-02 Valeo Climatisation Tubes d'echangeur thermique a plaques optimisees
EP1308687A1 (fr) * 2001-10-31 2003-05-07 Valeo Climatisation Tubes d'échangeur thermique à plaques optimisées
US6786276B2 (en) 2001-10-31 2004-09-07 Valeo Climatisation Heat exchanger tube with optimized plates
US6926075B2 (en) 2002-06-24 2005-08-09 Hitachi Air Conditioning Systems Co., Ltd. Plate type heat exchanger
CN100340834C (zh) * 2002-06-24 2007-10-03 日立空调系统株式会社 板式换热器
US7383687B2 (en) 2002-10-31 2008-06-10 Sharp Kabushiki Kaisha Regenerator method for manufacturing regenerator, system for manufacturing regenerator and stirling refrigerating machine
EP1500895A3 (fr) * 2003-07-22 2005-04-06 Modine Manufacturing Company Conduit pour échangeur de chaleur
JP2009210235A (ja) * 2008-03-06 2009-09-17 Panasonic Corp 熱交換器
JP2015528890A (ja) * 2012-07-27 2015-10-01 ゼネラル・エレクトリック・カンパニイ 空気冷却式のエンジン表面冷却器
JP2014040963A (ja) * 2012-08-22 2014-03-06 Daikin Ind Ltd 水熱交換器
RU2529288C1 (ru) * 2013-06-27 2014-09-27 Государственный научный центр Российской Федерации-федеральное государственное унитарное предприятие "Исследовательский Центр имени М.В. Келдыша" Пакет пластин теплообменного аппарата
EP3023727A1 (fr) * 2014-11-24 2016-05-25 Taiwan SRP Heat Exchanger Inc. Plaque de guidage de fluide et échangeur de plaque associé

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