WO2015020048A1 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
WO2015020048A1
WO2015020048A1 PCT/JP2014/070607 JP2014070607W WO2015020048A1 WO 2015020048 A1 WO2015020048 A1 WO 2015020048A1 JP 2014070607 W JP2014070607 W JP 2014070607W WO 2015020048 A1 WO2015020048 A1 WO 2015020048A1
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Prior art keywords
spiral
fluid
header
heat exchanger
spiral tube
Prior art date
Application number
PCT/JP2014/070607
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French (fr)
Japanese (ja)
Inventor
智規 原口
和田　博文
Original Assignee
サンデン株式会社
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Publication of WO2015020048A1 publication Critical patent/WO2015020048A1/en

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    • 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
    • F28D7/04—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 spirally coiled
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • 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
    • F28D9/04—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 being formed by spirally-wound plates or laminae

Definitions

  • the present invention relates to a heat exchanger that exchanges heat between a first fluid and a second fluid flowing in a spiral shape.
  • a spiral partition plate In exchanging heat between the first fluid and the second fluid having different temperatures, a spiral partition plate is provided in a cylindrical container to form a spiral passage between the partition plates, and a plurality of spiral tubes are provided in the spiral passage.
  • a spiral heat exchanger that is arranged to exchange heat by flowing a first fluid in a spiral passage and a second fluid in a spiral tube (see, for example, Patent Document 1).
  • FIG. 14 shows a plan view of the inside of a conventional spiral heat exchanger 100 according to the related art.
  • a spiral partition wall 103 and a spiral tube 104 are provided in the cylindrical container 102 of the heat exchanger 100.
  • the spiral tube 104 is disposed in close contact with the partition wall 103 in a plurality of stages.
  • a series of spiral passages 107 are formed between the spiral partition walls 103 and rotate outward from the center of the spiral, and the spiral pipe 104 is located in the spiral passage 107 and passes through the spiral passage 107. It arrange
  • the outer ends of the multi-stage spiral pipes 104 are communicated with a header 108, and the central ends of the spirals are also communicated with a header 109.
  • the first fluid for example, cold water
  • the first fluid flows in from the center of the spiral and flows out from the side surface of the container 102
  • the first fluid is transferred from the connection port 111 formed in the center of the spiral of the spiral passage 107 to the heat exchanger.
  • 100 flows in the spiral passage 107 while rotating counterclockwise from the center of the spiral toward the outside as indicated by an arrow in FIG. 14, and finally makes a round between the container 102 and the partition wall 103. It flows out of the heat exchanger 100 from the connection port 112 on the side surface 102.
  • a second fluid for example, a high-temperature refrigerant
  • the first fluid flows into the container 102 from the connection port 111 formed at the center of the spiral, and flows while rotating in the spiral passage 107 between the partition walls 103. In particular, it flows out from the connection port 112 formed on the side surface of the container 102. Therefore, between the header 109 on the center side and the spiral tube 104 and the partition wall 103 in the center portion of the spiral adjacent to the outer side of the header 109 (in the embodiment, the spiral tube 104 is inside the partition wall 103, so the spiral tube 104). A gap (indicated by X1 in FIG. 14) had to be formed.
  • a gap X2 must be formed between the outer header 108 and the partition wall 103 positioned inside the outer header 108, so that the diameter (body diameter) D2 of the container 102 is increased, and the pressure resistance is ensured. Therefore, the thickness has to be increased, and there has been a problem that the weight and cost are increased.
  • the present invention has been made to solve the conventional technical problems, and aims to reduce weight and cost by reducing the size of a so-called spiral heat exchanger.
  • the heat exchanger of the present invention comprises a spiral passage between spiral partition walls provided in a container, and a plurality of upper and lower spiral tube portions in contact with the spiral passage are provided. Heat exchange is performed between the first fluid flowing in the spiral passage outside the spiral tube portion and the second fluid flowing in the spiral tube portion, and includes a header provided at the end of the spiral tube portion, in the vicinity of the header.
  • the present invention is characterized in that a communication portion that connects the inner and outer spiral passages is formed.
  • the header is provided at each of the second fluid inlet side and outlet side end portions of the spiral tube portion, and the communication portion is any one of the headers, Or it is formed in the vicinity of both.
  • a heat exchanger includes a partition wall constituting the partition wall portion in each of the above inventions, and a spiral tube constituting the spiral tube portion, and the spiral tube is provided in close contact with the partition wall.
  • the communication wall is formed by terminating the partition wall in the vicinity of the header.
  • the partition wall portion and the spiral tube portion are integrally formed by extrusion, and the communicating portion is a partition wall portion other than the spiral tube portion. It is characterized by being deleted.
  • a heat exchanger is such that, in each of the above-mentioned inventions, the header located on the center side of the spiral is brought into contact with the adjacent partition wall portion or spiral tube portion and / or the header located outside the spiral. Is brought into contact with both an adjacent container and a partition wall portion or a spiral tube portion.
  • the partition wall portion and the spiral tube portion form an involute curve, and a line in contact with a base circle of the involute curve passes through the center of the header located outside the spiral. It is characterized by that.
  • the spiral tube portion is divided into a plurality of paths in which the second fluid reciprocates, and the second fluid flowing in the most downstream path is relative to the first fluid. It is characterized by having a counter flow.
  • the heat exchanger according to an eighth aspect of the present invention evaporates the second fluid in the above-described invention, and is characterized in that the number of spiral tube parts constituting the most downstream path is larger than that of the other paths.
  • the heat exchanger of the invention of claim 9 is characterized in that, in the above invention, a preheater is attached to the upstream side of the header on the inlet side of the second fluid, and the preheater and the first fluid on the downstream side are heat-exchanged.
  • the heat exchanger of the invention of claim 10 is characterized in that, in the above invention, the first fluid is allowed to flow out from the center of the vortex, and the preheater is arranged in a space in the container formed at the center of the vortex.
  • a heat exchanger according to an eleventh aspect of the present invention is the heat exchanger of the ninth aspect wherein the first fluid is allowed to flow from the center of the spiral and the preheater is disposed in the inner space of the container formed in the vicinity of the header located outside the spiral. It is characterized by.
  • a spiral passage is formed between spiral partition walls provided in a container, and a plurality of spiral tube portions in contact with the spiral passage are provided in the upper and lower stages to flow in the spiral passage outside the spiral tube portion.
  • a communication portion having a header provided at the end of the spiral tube portion and communicating the inner and outer spiral passages in the vicinity of the header Therefore, as in the invention of claim 2, the communication portion is formed in at least one of the headers provided at the end portions on the inlet side and the outlet side of the second fluid of the spiral tube portion, or in the vicinity of both.
  • the header located on the spiral side as in the invention of claim 5 is brought into contact with the adjacent partition wall portion or the spiral tube portion, and the header located outside the spiral is placed between the adjacent container and the partition wall.
  • the first fluid can flow between the internal and external spiral passages from the communicating part near the header without any problem even if it is brought into contact with both the pipe part and the spiral pipe part, and the diameter (body diameter) of the container is reduced. As a result, it is possible to reduce the weight and the cost by downsizing the heat exchanger.
  • the communicating portion may be formed by terminating the partition wall in the vicinity of the header, and when the partition wall portion and the spiral tube portion are integrally formed by extrusion as in the invention of claim 4, other than the spiral tube portion. Since the part of the partition wall part may be deleted to form the communication part, the workability of the communication part is improved.
  • partition wall portion and the spiral tube portion form an involute curve as in the invention of claim 6, if the line in contact with the basic circle of the involute curve passes through the center of the header located outside the spiral, It becomes possible to minimize the diameter (body diameter).
  • the spiral tube portion is divided into a plurality of paths in which the second fluid reciprocates, and the second fluid flowing in the most downstream path faces the first fluid. Since the heat exchanger is used as an evaporator, for example, when evaporating by heat exchange with the first fluid using the second fluid as a refrigerant, the most downstream path as in the invention of claim 8 By increasing the number of spiral tube parts that make up the other paths, the most downstream path with the largest number of spiral tube parts and the largest heat transfer area can be made a counterflow with improved heat exchange performance. It becomes possible to improve the heat exchange performance.
  • the second fluid becomes a gas-liquid two-phase, and the temperature is constant, so even if it is in parallel flow with the first fluid, it will not be different from the case of counterflow, and heat exchange performance will be reduced. Can be prevented.
  • the proportion of the gas phase increases toward the downstream, and the heat transfer rate is improved by increasing the flow velocity. Therefore, the deterioration of the heat exchange performance due to the parallel flow can be compensated for by improving the heat transfer coefficient, and the performance can be improved.
  • the heat exchanger when used as a condenser and the refrigerant as the second fluid is condensed by heat exchange with the first fluid, the second fluid is in the gas phase having a low heat transfer coefficient, The maximum temperature difference can be ensured, and the heat exchange performance can be improved even if the upstream side is cocurrent.
  • the heat exchanger when used as an evaporator to evaporate, for example, the refrigerant that is the second fluid, the temperature of the downstream path becomes higher as the refrigerant is warmed, and the temperature difference from the first fluid becomes smaller.
  • a preheater is attached to the upstream side of the header on the inlet side of the second fluid as in the invention of claim 9, and this preheater and the first fluid on the downstream side are connected. If heat exchange is performed, the heat of the first fluid can be effectively used by exchanging heat between the second fluid before flowing into the spiral tube portion of the heat exchanger and the first fluid having a high temperature. It becomes like this.
  • the preheater is inevitably formed at the center of the vortex by arranging the preheater in the space in the container formed at the center of the vortex.
  • the pre-heater is provided by using the space inside the container, and the enlargement of the dimensions can be prevented.
  • the pre-heater when the first fluid is allowed to flow from the center of the vortex, the pre-heater is disposed in the container inner space formed in the vicinity of the header located outside the vortex as in the invention of claim 11, thereby A pre-heater is provided by utilizing the space in the container that is inevitably formed in the vicinity, and the increase in size can be prevented.
  • FIG. 10 is a perspective view of the preheater of FIG. 9.
  • FIG. 10 is a perspective view of another embodiment of the preheater of FIG. 9. It is a figure explaining the pass ratio of a spiral tube when using the heat exchanger of FIG. 1 as a condenser. It is a top view inside the conventional spiral type heat exchanger.
  • reference numeral 1 denotes a spiral heat exchanger as an embodiment, and in the figure, a cylindrical container 2 whose top and bottom are opened, and a partition wall 3 as a spiral partition wall portion forming an involute curve, This is also composed of a spiral tube 4 as a spiral tube portion having an involute curve, and lids 6 and 6.
  • the container 2, the partition wall 3, the spiral tube 4 and the lid 6 are all made of metal such as stainless steel or aluminum, and the spiral tube 4 is arranged in a plurality of stages inside the partition wall 3 and is in close contact by brazing.
  • a partition wall 3 in which the spiral tubes 4 are in close contact with each other is arranged in the container 2, and the upper and lower openings of the container 2 are closed by lids 6 and 6.
  • the upper and lower ends of the partition wall 3 are in close contact with the inner surfaces of the lids 6 and 6, and the space between them is sealed.
  • a series of spiral passages 7 are formed between the spiral partition walls 3 toward the outside while rotating from the center of the spiral.
  • the spiral tube 4 is disposed in the spiral passage 7 so as to be in contact with the space in the spiral passage 7.
  • the spiral tube 4 comes into contact with a fluid (first fluid described later) flowing in the spiral passage 7.
  • the plurality of stages of the spiral tubes 4 are arranged with a space between each other, and as shown in FIG. 2, the outer end portions of the respective spiral tubes 4 (end portions on the inlet side of the second fluid in the embodiment). Is communicated with the header 8, and the end portion on the center side of the spiral (in the embodiment, the end portion on the outlet side of the second fluid) is also communicated with the header 9.
  • the spiral passage 7 is connected to the first fluid from a connection port 11 formed in the lid 6 in the vicinity (center portion) of the center of the spiral.
  • cold water flows into the heat exchanger 1.
  • the spiral passage 7 flows while rotating counterclockwise from the center of the spiral toward the outside as indicated by an arrow in FIG. 2, and flows out of the heat exchanger 1 from the connection port 12 formed on the side surface of the container 2.
  • a high-temperature refrigerant as the second fluid flows from the header 8 and flows in each spiral tube 4 while rotating clockwise from the outside in FIG. 2 toward the center of the spiral, and heat exchange from the header 9 It flows out of the vessel 1.
  • the flow of the cold water (first fluid) is counterclockwise in FIG. 3, and the flow of the refrigerant (second fluid) is counterclockwise, so the flow of the cold water and the refrigerant is generally opposite to each other. It becomes. Therefore, the temperature difference between the refrigerant flowing in the spiral tube 4 and the water flowing in the spiral path 7 outside the entire range extends from the header 8 on the inlet side of the refrigerant (second fluid) to the header 9 on the outlet side. It increases over time, improving the heat exchange performance. In particular, since the refrigerant (second fluid) flows through the spiral tube 4, high pressure resistance design is facilitated even when a high-pressure refrigerant flows.
  • the header 9 on the center side of the spiral is in contact with the spiral tube 4 adjacent to the outside, and the outer header 8 contacts both the container 2 adjacent to the outside and the partition wall 3 adjacent to the inside. Touching.
  • the spiral tube 4 is in close contact with the outer side of the partition wall 3
  • the header 9 is in contact with the partition wall 3 adjacent to the outer side
  • the header 8 is in contact with the spiral tube 4 adjacent to the inner side.
  • the diameter (body diameter) D1 of the container 2 becomes smaller than the diameter (body diameter) D2 of the container 102 of the conventional heat exchanger 100 of FIG.
  • the partition wall 3 ends in front of the header 8 and the header 9 and a space is formed between the header 8 and the header 9.
  • communication portions 13 and 14 communicating the inner and outer spiral passages 7 are formed in the vicinity of the headers 8 and 9, respectively.
  • the shape of the communication parts 13 and 14 is not limited to embodiment of FIG. 3,
  • a part of partition wall 3 can also be notched and formed.
  • cold water (first fluid) flows into the heat exchanger 1 from the connection port 11 formed at the center of the spiral of the spiral passage 7.
  • a space is formed at the center of the spiral, and the cold water (first fluid) that has flowed into the space flows out to the outer spiral passage 7 through the communication portion 14 formed in the vicinity of the header 9.
  • the spiral passage 7 flows while rotating counterclockwise from the center of the spiral toward the outside as indicated by an arrow in FIG. 2 and reaches the vicinity of the outer header 8.
  • the cold water (first fluid) flowing to the vicinity of the header 8 flows out to the space between the outer container 2 through the communication portion 13 formed in the vicinity of the header 8. Then, after making a round clockwise between the container 2 and the partition wall 3, it flows out of the heat exchanger 1 from the connection port 12 on the side surface of the container 2. Further, a high-temperature refrigerant (second fluid) flows from the header 8 and flows in each spiral tube 4 while rotating clockwise from the outside toward the center of the spiral in FIG. It flows out. Since the cold water (first fluid) and the refrigerant (second fluid) are opposed to each other, the heat exchange efficiency is increased.
  • the headers 8 and 9 provided at the refrigerant inlet side and outlet end portions of the spiral tube 4 are provided, and in the vicinity of each of the headers 8 and 9, a communication portion 13 that communicates the inner and outer spiral passages 7, 14 is formed, so that the cold water (first fluid) flowing in the spiral passage 7 between the central portion of the spiral and the side surface of the container 2 passes through the communication portions 13 and 14 in the vicinity of the headers 8 and 9 and It becomes possible to flow between the outer spiral passages 7.
  • the header 9 located in the center side of the spiral is brought into contact with the adjacent spiral tube 4 (or the partition wall 3) as in the embodiment, and the header 8 positioned outside the spiral is connected to the adjacent container 2.
  • the partition wall 3 (or the spiral tube 4) is brought into contact with each other, the cold water (first fluid) flows between the communication portions 13 and 14 near the headers 8 and 9 between the inner and outer spiral passages 7 without any trouble.
  • the diameter (body diameter) D1 of the container 2 can be reduced to reduce the weight and the cost by downsizing the heat exchanger 1.
  • FIG. 4 shows a plan view of the inside of the heat exchanger 1 of another embodiment.
  • This embodiment is an example in which the partition wall portion 3A and the spiral tube portion 4A corresponding to the partition wall 3 and the spiral tube 4 in the above-described embodiment are integrally formed with the extruded material 15 by extrusion molding of a metal such as aluminum. is there.
  • the extruded material 15 of the embodiment is formed with a plurality of upper and lower spiral tube portions 4A having a circular passage in the inside, and each spiral tube portion 4A is mutually connected by a partition wall portion 3A located between them. Connected configuration.
  • path 7 is comprised between the inner and outer partition wall part 3A and the spiral pipe part 4A by winding the flat extrusion material 15 which concerns on this Example in spiral shape so that an involute curve may be comprised.
  • the spiral-side header 9 is in contact with the spiral tube portion 4A adjacent to the outside, and the outer header 8 is formed between the container 2 adjacent to the outside and the spiral tube portion 4A adjacent to the inside. It is in contact with both sides.
  • the communication portions 13 and 14 are formed by deleting the partition wall portion 3A between the upper and lower spiral tube portions 4A in the vicinity of the headers 8 and 9. Thereby, the size of the heat exchanger 1 can be reduced while securing the flow of cold water (first fluid) as in the above-described embodiment.
  • FIG. 5 shows another example for defining the positions of the partition walls 3A and the spiral pipes 4A of the headers 8 and 9 in FIG. 4 forming the involute curve as described above.
  • the line L1 in contact with the basic circle CB of the involute curve passes through the center of the header 8 located outside the spiral.
  • the involute curve is a curve drawn by the end point of a thread when the thread wound around the base circle CB (reel) is stretched straight without rotating the base circle CB itself.
  • the line L1 is in contact with the unwinding side of the basic circle CB (it is placed on the yarn).
  • the communication portions 13 and 14 are formed in the vicinity of both the header 8 and the header 9, but may be formed in either one. In that case, it is necessary to separate the header not formed from the spiral tube (vortex tube portion) or the partition wall (partition wall portion), but at least the diameter (body diameter) of the container can be reduced as compared with the case of FIG. .
  • FIGS. 6 to 8 show an example in which the spiral tube 4 (vortex tube portion 4A) through which the refrigerant (second fluid) flows is divided.
  • 6 to 8 use the heat exchanger 1 as an evaporator to exchange heat between the coolant as the second fluid and the water (hot water) as the first fluid in the spiral tube 4 (vortex tube portion 4A). Evaporate.
  • the water (first fluid) then flows into the spiral passage 7 from the outer connection port 12 and flows out from the connection port 11 on the center side of the spiral.
  • the refrigerant (second fluid) flows in from the lower part of the header 9 on the spiral side and flows out from the upper part of the outer header 8.
  • the first fluid is water (in this case, warm water) and the second fluid is a refrigerant.
  • the flow rate difference between the first fluid and the second fluid is large, and the flow rate of the first fluid> the flow rate of the second fluid.
  • it is effective to reduce the flow path area and increase the flow velocity by performing the pass division only for the second fluid.
  • the heat exchange amount Q per unit time of the heat exchanger is obtained by Expression (1).
  • Q [W] U [W / m 2 ⁇ K] ⁇ A [m 2 ] ⁇ ⁇ T [° C.] (1)
  • U is the overall heat transfer coefficient
  • A is the heat transfer area
  • ⁇ T is the effective temperature difference between the first fluid and the second fluid.
  • the effective temperature difference ⁇ T is expressed by the equation (2).
  • the counter flow has a larger value than the parallel flow, and the counter flow has a larger heat exchange amount Q than the parallel flow.
  • any of the paths is always in parallel with the first fluid.
  • a decrease in performance occurs due to a decrease in effective temperature difference ⁇ T.
  • the temperature of the inlet second fluid (refrigerant) increases, and the effective temperature difference ⁇ T decreases.
  • the plurality of spiral tubes 4 are divided into three paths PS1, PS2, and PS3 from the bottom.
  • the number of spiral tubes 4 is such that the path PS1 ⁇ the path PS2 ⁇ the path PS3, and the headers 8 and 9 are partitioned 16 so that the path PS1 is the most upstream, then the path PS2, and the path PS3 is the most downstream. Partition with.
  • the bold arrow indicates the flow of the refrigerant that is the second fluid
  • the white arrow indicates the flow of the water (hot water) that is the first fluid.
  • the refrigerant flowing in from the lower part of the header 9 on the center side of the spiral enters the uppermost path PS1 at the lowermost part, flows in the spiral pipe 4 constituting the path PS1 toward the header 8 (forward path), and then from the header 8 Enters the path PS2 that is one level above, flows in the spiral 4 constituting the path PS2 toward the header 9 (return path), enters the path PS3 that is the most downstream from the header 9, and constitutes the path PS3. It flows toward the header 8 and flows out (outward path). Therefore, the second fluid in the path PS1 is a counterflow with respect to the first fluid, a parallel flow is in the path PS2, and a counterflow is in the path PS3.
  • FIG. 7 shows the state of the refrigerant (second fluid) in each pass.
  • the refrigerant flowing into the path PS1 from the header 9 is in a liquid phase, gradually evaporates toward the header 8, and becomes a gas-liquid two phase. Although it further evaporates in the process of flowing through the path PS2, it passes through the path PS2 to the header 9 in a gas-liquid two-phase state, and further evaporates in the process of flowing to the header 8 in the path PS3, so that all of the gas-liquid two-phase is changed into the gas phase Change.
  • the spiral tube 4 is divided into three paths PS1 to PS3 through which the second fluid reciprocates, and the second fluid flowing through the most downstream path PS3 is configured to face the first fluid. ing. Since the number of the spiral tubes 4 in the most downstream path PS3 is larger than that in the other paths, the heat exchanger 1 is used as an evaporator as in the embodiment, and the second fluid is used as a refrigerant and the first fluid. When evaporating by heat exchange with (warm water), the most downstream path PS3 having the largest number of spiral tubes 4 and the largest heat transfer area becomes a counter flow with improved heat exchange performance, and heat exchange of the heat exchanger 1 is performed. The performance can be improved.
  • the refrigerant (second fluid) in a gas-liquid two-phase and the temperature is constant, so that even if it is in parallel flow with the first fluid (warm water), it is different from the counterflow case. It is possible to prevent a decrease in heat exchange performance.
  • the proportion of the gas phase increases toward the downstream, and the heat transfer rate is improved by increasing the flow velocity. Therefore, the deterioration of the heat exchange performance due to the parallel flow can be compensated for by improving the heat transfer coefficient, and the performance can be improved.
  • FIG. 8 shows the temperature of the refrigerant (second fluid) in each part in the examples of FIGS.
  • the temperature difference between the hot water (first fluid) and the refrigerant (second fluid) becomes small, so the temperature of the hot water on the downstream side (center side of the spiral) is the heat exchanger 1. It is low in the lower part of the water, but higher in the upper part, and the heat flows out without being used.
  • a preheater 17 is attached to the upstream side of the header 9 serving as the refrigerant (second fluid) inlet side, and the preheater 17 is heated from the lower side to the hot water (first fluid) and from the lower part to the upper part. It arrange
  • the preheater 17 is attached to the upstream side of the header 9 on the inlet side of the refrigerant (second fluid) and heat is exchanged between the preheater 17 and the hot water (first fluid) on the downstream side, heat exchange is performed. It is possible to effectively use the heat of the first fluid by exchanging heat with the refrigerant (second fluid) before flowing into the spiral tube 4 of the vessel 1 and the hot water (first fluid) at the upper part of this temperature. become.
  • FIG. 10 shows an arrangement example of the preheater 17 on the heat exchanger 1.
  • the partition wall 3 and the spiral tube 4 are arranged in a space in the container 2 formed at the center of the spiral. This space is downstream of the hot water (first fluid).
  • the preheater 17 is provided using the space in the container 2 that is inevitably formed at the center of the spiral, and the expansion of the dimensions of the container 2 can be prevented.
  • FIG. 11 and 12 show an example of the configuration of the preheater 17.
  • FIG. 11 shows a case where the preheater 17 is constituted by a spiral pipe
  • FIG. 12 shows a case where the preheater 17 is constituted by a pipe having innumerable protrusions 18 attached thereto.
  • the first fluid in this case, warm water because it is an evaporator
  • the first fluid flows in from the center side of the spiral and flows out from the container 2 side as in the case of FIG.
  • the header 8 located outside the refrigerant becomes the refrigerant inlet side
  • the space in the container 2 formed in the vicinity of the header 8 located outside the vortex of the preheater 17 (the space SX surrounded by a broken circle in FIG. 2) ).
  • the preheater can be provided using the space inside the container that is inevitably formed near the outer header, and the size can be prevented from increasing.
  • FIG. 13 shows a pass ratio when the heat exchanger 1 is used as a condenser as in FIG.
  • the plurality of spiral tubes 4 are divided into two paths PS4 and PS5 from the top. Then, the number of spiral tubes 4 is such that path PS5 ⁇ path PS4, and the headers 8 and 9 are partitioned by a partition 16 so that the path PS4 is upstream and the path PS5 is downstream.
  • the bold arrow indicates the flow of the refrigerant that is the second fluid
  • the white arrow indicates the flow of the water that is the first fluid (in this case, cold water).
  • the refrigerant flowing into the path PS4 from the header 9 is in a gas phase (temperature is + 65 ° C.), and gradually condenses with cold water (first fluid) of about + 15 ° C. toward the header 8 to become a gas-liquid two phase. . And at the time of further condensing in the process of flowing through the path PS5 and returning to the header 9, it becomes a liquid-rich gas-liquid two phase.
  • the refrigerant (second fluid) has a heat transfer coefficient.
  • the maximum temperature difference with the cold water (first fluid) can be secured, and the heat exchange performance can be improved even if the upstream path PS4 becomes a parallel flow.
  • the Example demonstrated the heat exchanger which implement
  • the present invention is applied to the spiral heat exchanger of all uses. It is valid.
  • the first fluid is water (cold water or hot water) and the second fluid is a refrigerant.
  • the heat exchanger of the present invention can be used for heat exchange between various fluids having temperature differences. It is.
  • Heat exchanger 2 Container 3 Partition wall (partition wall) 3A Partition wall 4 Swirl tube (Swirl tube) 4A spiral tube portion 6 lid 7 spiral passage 8, 9 header 11, 12 connection port 13, 14 communication portion 17 preheater

Abstract

[Problem] To effect a reduction in cost and weight resulting from increased compactness in a so-called spiral heat exchanger. [Solution] This heat exchanger (1) is such that a spiraling channel (7) is configured between spiral partitions (3) provided within a cylindrical vessel (2), a vertical plurality of spiraling tubes (4) that contact the spiraling channel (7) are provided, and heat is exchanged between a first fluid flowing within the spiraling channel (7) at the outside of the spiraling tubes (4) and a second fluid flowing within the spiraling tubes (4). A header (8) and header (9) are provided to the ends of the spiraling tubes (4), and an inner and outer interconnection section (13) and interconnection section (14) that interconnect with the spiraling channel (7) are formed in the vicinity of the header (8) and header (9).

Description

熱交換器Heat exchanger
　本発明は、渦巻状に流れる第一流体と第二流体とを熱交換させる熱交換器に関する。 The present invention relates to a heat exchanger that exchanges heat between a first fluid and a second fluid flowing in a spiral shape.
　温度の異なる第一流体と第二流体とを熱交換させるに当たり、円筒状の容器内に渦巻状の仕切板を設けて仕切板間に渦巻通路を構成し、この渦巻通路に渦巻管を複数段配置し、渦巻通路に第一流体を、渦巻管内に第二流体をそれぞれ流して熱交換させる渦巻型熱交換器が知られている（例えば、特許文献１参照）。 In exchanging heat between the first fluid and the second fluid having different temperatures, a spiral partition plate is provided in a cylindrical container to form a spiral passage between the partition plates, and a plurality of spiral tubes are provided in the spiral passage. There is known a spiral heat exchanger that is arranged to exchange heat by flowing a first fluid in a spiral passage and a second fluid in a spiral tube (see, for example, Patent Document 1).
　ここで、図１４は従来の係る渦巻型の熱交換器１００の内部の平面図を示している。熱交換器１００の円筒状の容器１０２内には、渦巻状の仕切壁１０３と、渦巻管１０４が設けられている。渦巻管１０４は仕切壁１０３の内側に複数段配置されて密着されている。そして、渦巻状の仕切壁１０３間には、渦巻の中心から回転しながら外側に向かう一連の渦巻通路１０７が構成され、渦巻管１０４はこの渦巻通路１０７内に位置して当該渦巻通路１０７内を流れる第一流体と接するように配置される。また、複数段の渦巻管１０４の外側の端部はヘッダ１０８で連通され、渦巻の中心側の端部もヘッダ１０９で連通されている。 Here, FIG. 14 shows a plan view of the inside of a conventional spiral heat exchanger 100 according to the related art. In the cylindrical container 102 of the heat exchanger 100, a spiral partition wall 103 and a spiral tube 104 are provided. The spiral tube 104 is disposed in close contact with the partition wall 103 in a plurality of stages. A series of spiral passages 107 are formed between the spiral partition walls 103 and rotate outward from the center of the spiral, and the spiral pipe 104 is located in the spiral passage 107 and passes through the spiral passage 107. It arrange | positions so that the flowing 1st fluid may be touched. Further, the outer ends of the multi-stage spiral pipes 104 are communicated with a header 108, and the central ends of the spirals are also communicated with a header 109.
　そして、第一流体（例えば冷水）を渦巻の中心部から流入させて容器１０２の側面から流出させる場合、渦巻通路１０７の渦巻の中心部に形成された接続口１１１から第一流体が熱交換器１００内に流入し、渦巻通路１０７を図１４中矢印で示すように渦巻の中心から外側に向けて反時計回りに回転しながら流れ、最後は容器１０２と仕切壁１０３間を一周した後、容器１０２の側面の接続口１１２から熱交換器１００外に流出することになる。また、ヘッダ１０８からは第二流体（例えば高温の冷媒）が流入し、各渦巻管１０４内を図１４中時計回りに外側から渦巻の中心に向けて回転しながら流れ、ヘッダ１０９から熱交換器１００外に流出するものであった。このように、第一流体と第二流体とは対向流となるので、熱交換効率が高くコンパクトな熱交換器とすることができる利点がある。 When the first fluid (for example, cold water) flows in from the center of the spiral and flows out from the side surface of the container 102, the first fluid is transferred from the connection port 111 formed in the center of the spiral of the spiral passage 107 to the heat exchanger. 100, flows in the spiral passage 107 while rotating counterclockwise from the center of the spiral toward the outside as indicated by an arrow in FIG. 14, and finally makes a round between the container 102 and the partition wall 103. It flows out of the heat exchanger 100 from the connection port 112 on the side surface 102. Further, a second fluid (for example, a high-temperature refrigerant) flows from the header 108 and flows in each spiral tube 104 while rotating clockwise from the outside toward the center of the spiral in FIG. It flowed out of 100. Thus, since the 1st fluid and the 2nd fluid become countercurrent, there is an advantage which can be set as a compact heat exchanger with high heat exchange efficiency.
特開２００６－１６２１５７号公報JP 2006-162157 A
　このように渦巻型の熱交換器１００では渦巻の中心部に形成された接続口１１１から第一流体が容器１０２内に流入し、仕切壁１０３間の渦巻通路１０７内を回転しながら流れて最終的に容器１０２の側面に形成された接続口１１２から流出するものであった。そのため、中心側のヘッダ１０９とそれの外側に隣接する渦巻の中心部における渦巻管１０４や仕切壁１０３（実施例では渦巻管１０４が仕切壁１０３の内側にあるので渦巻管１０４）との間に隙間（図１４にＸ１で示す）を形成しなければならなかった。 Thus, in the spiral heat exchanger 100, the first fluid flows into the container 102 from the connection port 111 formed at the center of the spiral, and flows while rotating in the spiral passage 107 between the partition walls 103. In particular, it flows out from the connection port 112 formed on the side surface of the container 102. Therefore, between the header 109 on the center side and the spiral tube 104 and the partition wall 103 in the center portion of the spiral adjacent to the outer side of the header 109 (in the embodiment, the spiral tube 104 is inside the partition wall 103, so the spiral tube 104). A gap (indicated by X1 in FIG. 14) had to be formed.
　また、外側のヘッダ１０８とその内側に位置する仕切壁１０３との間にも隙間Ｘ２を形成しなければならず、そのため、容器１０２の直径（胴径）Ｄ２が拡大されてしまい、耐圧確保のために肉厚にしなければならず、重量とコストが増大するという問題が発生していた。 In addition, a gap X2 must be formed between the outer header 108 and the partition wall 103 positioned inside the outer header 108, so that the diameter (body diameter) D2 of the container 102 is increased, and the pressure resistance is ensured. Therefore, the thickness has to be increased, and there has been a problem that the weight and cost are increased.
　本発明は、係る従来の技術的課題を解決するために成されたものであり、所謂渦巻型の熱交換器において、小型化による重量とコストの削減を図ることを目的とする。 The present invention has been made to solve the conventional technical problems, and aims to reduce weight and cost by reducing the size of a so-called spiral heat exchanger.
　上記課題を解決するために、本発明の熱交換器は、容器内に設けられた渦巻状の仕切壁部間に渦巻通路を構成し、この渦巻通路に接する渦巻管部を上下複数段設けて渦巻管部外側の渦巻通路内を流れる第一流体と渦巻管部内を流れる第二流体とを熱交換させるものであって、渦巻管部の端部に設けられたヘッダを備え、このヘッダ近傍に、内外の渦巻通路を連通する連通部を形成したことを特徴とする。 In order to solve the above problems, the heat exchanger of the present invention comprises a spiral passage between spiral partition walls provided in a container, and a plurality of upper and lower spiral tube portions in contact with the spiral passage are provided. Heat exchange is performed between the first fluid flowing in the spiral passage outside the spiral tube portion and the second fluid flowing in the spiral tube portion, and includes a header provided at the end of the spiral tube portion, in the vicinity of the header. In addition, the present invention is characterized in that a communication portion that connects the inner and outer spiral passages is formed.
　請求項２の発明の熱交換器は、上記発明においてヘッダは、渦巻管部の第二流体の入口側と出口側の端部にそれぞれ設けられ、連通部は各ヘッダのうちの何れか一方、若しくは、双方の近傍に形成されていることを特徴とする。 In the heat exchanger of the invention of claim 2, in the above invention, the header is provided at each of the second fluid inlet side and outlet side end portions of the spiral tube portion, and the communication portion is any one of the headers, Or it is formed in the vicinity of both.
　請求項３の発明の熱交換器は、上記各発明において仕切壁部を構成する仕切壁と、渦巻管部を構成する渦巻管とを備え、この渦巻管が仕切壁に密着して設けられると共に、仕切壁をヘッダの近傍で終了させることにより、連通部が形成されていることを特徴とする。 A heat exchanger according to a third aspect of the present invention includes a partition wall constituting the partition wall portion in each of the above inventions, and a spiral tube constituting the spiral tube portion, and the spiral tube is provided in close contact with the partition wall. The communication wall is formed by terminating the partition wall in the vicinity of the header.
　請求項４の発明の熱交換器は、請求項１又は請求項２の発明において仕切壁部と渦巻管部は一体に押出成形されており、連通部は渦巻管部以外の部分の仕切壁部を削除して形成されていることを特徴とする。 According to a fourth aspect of the present invention, in the first or second aspect of the invention, the partition wall portion and the spiral tube portion are integrally formed by extrusion, and the communicating portion is a partition wall portion other than the spiral tube portion. It is characterized by being deleted.
　請求項５の発明の熱交換器は、上記各発明において渦巻の中心側に位置するヘッダを、隣接する仕切壁部若しくは渦巻管部に当接させ、及び／又は、渦巻の外側に位置するヘッダを、隣接する容器と、仕切壁部若しくは渦巻管部の双方に当接させたことを特徴とする。 A heat exchanger according to a fifth aspect of the present invention is such that, in each of the above-mentioned inventions, the header located on the center side of the spiral is brought into contact with the adjacent partition wall portion or spiral tube portion and / or the header located outside the spiral. Is brought into contact with both an adjacent container and a partition wall portion or a spiral tube portion.
　請求項６の発明の熱交換器は、上記発明において仕切壁部及び渦巻管部はインボリュート曲線を成し、このインボリュート曲線の基礎円に接する線が渦巻の外側に位置するヘッダの中心を通るようにしたことを特徴とする。 In the heat exchanger of the invention of claim 6, in the above invention, the partition wall portion and the spiral tube portion form an involute curve, and a line in contact with a base circle of the involute curve passes through the center of the header located outside the spiral. It is characterized by that.
　請求項７の発明の熱交換器は、上記各発明において渦巻管部は第二流体が往復して流れる複数のパスに分けられ、最も下流のパスを流れる第二流体が第一流体に対して対向流となるように構成したことを特徴とする。 In the heat exchanger of the invention of claim 7, in each of the above inventions, the spiral tube portion is divided into a plurality of paths in which the second fluid reciprocates, and the second fluid flowing in the most downstream path is relative to the first fluid. It is characterized by having a counter flow.
　請求項８の発明の熱交換器は、上記発明において第二流体を蒸発させるものであり、最も下流のパスを構成する渦巻管部の数を他のパスより多くしたことを特徴とする。 The heat exchanger according to an eighth aspect of the present invention evaporates the second fluid in the above-described invention, and is characterized in that the number of spiral tube parts constituting the most downstream path is larger than that of the other paths.
　請求項９の発明の熱交換器は、上記発明において第二流体の入口側のヘッダの上流側にプリヒータを取り付け、このプリヒータと下流側の第一流体とを熱交換させることを特徴とする。 The heat exchanger of the invention of claim 9 is characterized in that, in the above invention, a preheater is attached to the upstream side of the header on the inlet side of the second fluid, and the preheater and the first fluid on the downstream side are heat-exchanged.
　請求項１０の発明の熱交換器は、上記発明において第一流体を渦巻の中心から流出させると共に、プリヒータを渦巻の中心に形成される容器内空間に配置したことを特徴とする。 The heat exchanger of the invention of claim 10 is characterized in that, in the above invention, the first fluid is allowed to flow out from the center of the vortex, and the preheater is arranged in a space in the container formed at the center of the vortex.
　請求項１１の発明の熱交換器は、請求項９の発明において第一流体を渦巻の中心から流入させると共に、プリヒータを渦巻の外側に位置するヘッダ近傍に形成される容器内空間に配置したことを特徴とする。 A heat exchanger according to an eleventh aspect of the present invention is the heat exchanger of the ninth aspect wherein the first fluid is allowed to flow from the center of the spiral and the preheater is disposed in the inner space of the container formed in the vicinity of the header located outside the spiral. It is characterized by.
　本発明によれば、容器内に設けられた渦巻状の仕切壁部間に渦巻通路を構成し、この渦巻通路に接する渦巻管部を上下複数段設けて渦巻管部外側の渦巻通路内を流れる第一流体と渦巻管部内を流れる第二流体とを熱交換させる熱交換器において、渦巻管部の端部に設けられたヘッダを備え、このヘッダ近傍に、内外の渦巻通路を連通する連通部を形成したので、請求項２の発明のように渦巻管部の第二流体の入口側と出口側の端部にそれぞれ設けられるヘッダの少なくとも一方、若しくは、双方の近傍に連通部を形成することで、渦巻の中心部と容器の側面との間で渦巻通路内を流通する第一流体が、ヘッダ近傍の連通部を経て内側と外側の渦巻通路間を流れることができるようになる。 According to the present invention, a spiral passage is formed between spiral partition walls provided in a container, and a plurality of spiral tube portions in contact with the spiral passage are provided in the upper and lower stages to flow in the spiral passage outside the spiral tube portion. In the heat exchanger for exchanging heat between the first fluid and the second fluid flowing in the spiral tube portion, a communication portion having a header provided at the end of the spiral tube portion and communicating the inner and outer spiral passages in the vicinity of the header Therefore, as in the invention of claim 2, the communication portion is formed in at least one of the headers provided at the end portions on the inlet side and the outlet side of the second fluid of the spiral tube portion, or in the vicinity of both. Thus, the first fluid flowing in the spiral passage between the central portion of the spiral and the side surface of the container can flow between the inner and outer spiral passages via the communication portion near the header.
　これにより、請求項５の発明の如く渦巻の中心側に位置するヘッダを、隣接する仕切壁部若しくは渦巻管部に当接させ、渦巻の外側に位置するヘッダを、隣接する容器と、仕切壁部若しくは渦巻管部の双方に当接させたとしても、第一流体は支障無くヘッダ近傍の連通部から内外の渦巻通路間を流れることができるようになり、容器の直径（胴径）を縮小して熱交換器の小型化による重量の低減とコストの削減を図ることができるようになる。 Thus, the header located on the spiral side as in the invention of claim 5 is brought into contact with the adjacent partition wall portion or the spiral tube portion, and the header located outside the spiral is placed between the adjacent container and the partition wall. The first fluid can flow between the internal and external spiral passages from the communicating part near the header without any problem even if it is brought into contact with both the pipe part and the spiral pipe part, and the diameter (body diameter) of the container is reduced. As a result, it is possible to reduce the weight and the cost by downsizing the heat exchanger.
　この場合、請求項３の発明の如く仕切壁部を構成する仕切壁と、渦巻管部を構成する渦巻管とを備え、この渦巻管が仕切壁に密着して設けられる熱交換器においては、仕切壁をヘッダの近傍で終了させることにより連通部を形成すればよく、請求項４の発明の如く仕切壁部と渦巻管部が一体に押出成形されている場合には、渦巻管部以外の部分の仕切壁部を削除して連通部を形成すればよいので、該連通部の加工性が向上する。 In this case, in the heat exchanger provided with the partition wall constituting the partition wall portion as in the invention of claim 3 and the spiral tube constituting the spiral tube portion, the spiral tube being provided in close contact with the partition wall, The communicating portion may be formed by terminating the partition wall in the vicinity of the header, and when the partition wall portion and the spiral tube portion are integrally formed by extrusion as in the invention of claim 4, other than the spiral tube portion. Since the part of the partition wall part may be deleted to form the communication part, the workability of the communication part is improved.
　更に、請求項６の発明の如く仕切壁部及び渦巻管部がインボリュート曲線を成す場合、インボリュート曲線の基礎円に接する線が渦巻の外側に位置するヘッダの中心を通るようにすれば、容器の直径（胴径）を最小とすることが可能となる。 Further, when the partition wall portion and the spiral tube portion form an involute curve as in the invention of claim 6, if the line in contact with the basic circle of the involute curve passes through the center of the header located outside the spiral, It becomes possible to minimize the diameter (body diameter).
　請求項７の発明によれば上記各発明に加えて、渦巻管部を第二流体が往復して流れる複数のパスに分け、最も下流のパスを流れる第二流体が第一流体に対して対向流となるように構成したので、熱交換器を蒸発器として使用し、例えば第二流体を冷媒として第一流体との熱交換で蒸発させるときには、請求項８の発明の如くに最も下流のパスを構成する渦巻管部の数を他のパスより多くすることで、最も渦巻管部の数が多く伝熱面積が最大となる最下流のパスを、熱交換性能が高まる対向流とすることができるようになり、熱交換性能の向上を図ることが可能となる。 According to the invention of claim 7, in addition to the above inventions, the spiral tube portion is divided into a plurality of paths in which the second fluid reciprocates, and the second fluid flowing in the most downstream path faces the first fluid. Since the heat exchanger is used as an evaporator, for example, when evaporating by heat exchange with the first fluid using the second fluid as a refrigerant, the most downstream path as in the invention of claim 8 By increasing the number of spiral tube parts that make up the other paths, the most downstream path with the largest number of spiral tube parts and the largest heat transfer area can be made a counterflow with improved heat exchange performance. It becomes possible to improve the heat exchange performance.
　また、最下流よりも上流のパスでは第二流体は気液二相となり、温度が一定となるので、第一流体と並流となっても対向流の場合と変わらなくなり、熱交換性能の低下を防止できる。更に、気液二相のパスでは下流ほど気相の占める割合が高まり、流速が増すことで熱伝達率が向上する。従って、並流となることによる熱交換性能の低下を、熱伝達率の向上により補い、性能の改善を図ることができる。 In addition, in the path upstream from the most downstream, the second fluid becomes a gas-liquid two-phase, and the temperature is constant, so even if it is in parallel flow with the first fluid, it will not be different from the case of counterflow, and heat exchange performance will be reduced. Can be prevented. Further, in the gas-liquid two-phase path, the proportion of the gas phase increases toward the downstream, and the heat transfer rate is improved by increasing the flow velocity. Therefore, the deterioration of the heat exchange performance due to the parallel flow can be compensated for by improving the heat transfer coefficient, and the performance can be improved.
　一方、熱交換器を凝縮器として使用し、第二流体である冷媒を第一流体との熱交換で凝縮させる場合にも、第二流体が熱伝達率の低い気相において、第一流体との最大の温度差を確保することができ、上流側が並流となっても熱交換性能を向上させることが可能となる。 On the other hand, when the heat exchanger is used as a condenser and the refrigerant as the second fluid is condensed by heat exchange with the first fluid, the second fluid is in the gas phase having a low heat transfer coefficient, The maximum temperature difference can be ensured, and the heat exchange performance can be improved even if the upstream side is cocurrent.
　ここで、熱交換器を蒸発器として使用し、第二流体である例えば冷媒を蒸発させる場合、冷媒が温められて下流のパスほど温度が高くなり、第一流体との温度差が小さくなって出口側の第一流体の温度が位置によって異なって来るが、請求項９の発明の如く第二流体の入口側のヘッダの上流側にプリヒータを取り付け、このプリヒータと下流側の第一流体とを熱交換させるようにすれば、熱交換器の渦巻管部に流入する前の第二流体と、この温度の高い第一流体と熱交換させて第一流体の熱を有効に利用することができるようになる。 Here, when the heat exchanger is used as an evaporator to evaporate, for example, the refrigerant that is the second fluid, the temperature of the downstream path becomes higher as the refrigerant is warmed, and the temperature difference from the first fluid becomes smaller. Although the temperature of the first fluid on the outlet side varies depending on the position, a preheater is attached to the upstream side of the header on the inlet side of the second fluid as in the invention of claim 9, and this preheater and the first fluid on the downstream side are connected. If heat exchange is performed, the heat of the first fluid can be effectively used by exchanging heat between the second fluid before flowing into the spiral tube portion of the heat exchanger and the first fluid having a high temperature. It becomes like this.
　この場合、請求項１０の発明の如く第一流体を渦巻の中心から流出させる場合には、プリヒータを渦巻の中心に形成される容器内空間に配置することにより、渦巻の中心部にどうしても形成されてしまう容器内空間を利用してプリヒータを設け、寸法の拡大を防止することができるようになる。 In this case, when the first fluid flows out from the center of the vortex as in the invention of claim 10, the preheater is inevitably formed at the center of the vortex by arranging the preheater in the space in the container formed at the center of the vortex. The pre-heater is provided by using the space inside the container, and the enlargement of the dimensions can be prevented.
　逆に、第一流体を渦巻の中心から流入させる場合には、請求項１１の発明の如くプリヒータを渦巻の外側に位置するヘッダ近傍に形成される容器内空間に配置することにより、外側のヘッダ近傍にどうしても形成されてしまう容器内空間を利用してプリヒータを設け、寸法の拡大を防止することができるようになる。 Conversely, when the first fluid is allowed to flow from the center of the vortex, the pre-heater is disposed in the container inner space formed in the vicinity of the header located outside the vortex as in the invention of claim 11, thereby A pre-heater is provided by utilizing the space in the container that is inevitably formed in the vicinity, and the increase in size can be prevented.
本発明を適用した一実施例の熱交換器の分解斜視図である。It is a disassembled perspective view of the heat exchanger of one Example to which this invention is applied. 図１の熱交換器内部の平面図である。It is a top view inside the heat exchanger of FIG. 図１の熱交換器の仕切壁と渦巻管の斜視図である。It is a perspective view of the partition wall and spiral tube of the heat exchanger of FIG. 本発明の他の実施例の熱交換器内部の平面図である。It is a top view inside the heat exchanger of the other Example of this invention. 図４の熱交換器のインボリュート曲線の基礎円と外側のヘッダとの位置関係を説明する図である。It is a figure explaining the positional relationship of the basic circle of the involute curve of the heat exchanger of FIG. 4, and an outer header. 図１の熱交換器を蒸発器として使用するときの、渦巻管のパス割を説明する図である。It is a figure explaining the pass ratio of a spiral tube when using the heat exchanger of FIG. 1 as an evaporator. 図６における第二流体である冷媒の各部の状態を説明する図である。It is a figure explaining the state of each part of the refrigerant | coolant which is the 2nd fluid in FIG. 図６における第二流体である冷媒の各部の温度を説明する図である。It is a figure explaining the temperature of each part of the refrigerant | coolant which is the 2nd fluid in FIG. 本発明のもう一つの他の実施例の熱交換器の第一流体と第二流体の流れを示す図である。It is a figure which shows the flow of the 1st fluid and 2nd fluid of the heat exchanger of another another Example of this invention. 図９の熱交換器内部の斜視図である。It is a perspective view inside the heat exchanger of FIG. 図９のプリヒータの斜視図である。FIG. 10 is a perspective view of the preheater of FIG. 9. 図９のプリヒータのもう一つの実施例の斜視図である。FIG. 10 is a perspective view of another embodiment of the preheater of FIG. 9. 図１の熱交換器を凝縮器として使用するときの、渦巻管のパス割を説明する図である。It is a figure explaining the pass ratio of a spiral tube when using the heat exchanger of FIG. 1 as a condenser. 従来の渦巻型の熱交換器内部の平面図である。It is a top view inside the conventional spiral type heat exchanger.
　以下、本発明の実施の形態について、図面に基づき詳細に説明する。 Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
　図１において、１は実施例である渦巻型の熱交換器であり、図中において上下が開口した円筒状の容器２と、インボリュート曲線を成す渦巻状の仕切壁部としての仕切壁３と、これもインボリュート曲線を成す渦巻管部としての渦巻管４と、蓋６、６とから構成されている。これら容器２、仕切壁３、渦巻管４及び蓋６は何れもステンレスやアルミニウム等の金属製であり、渦巻管４は仕切壁３の内側に複数段配置され、ろう付けにより密着されている。そして、この渦巻管４が複数段密着された仕切壁３が容器２内に配置され、容器２の上下の開口を蓋６、６にて閉塞することにより構成されている。 In FIG. 1, reference numeral 1 denotes a spiral heat exchanger as an embodiment, and in the figure, a cylindrical container 2 whose top and bottom are opened, and a partition wall 3 as a spiral partition wall portion forming an involute curve, This is also composed of a spiral tube 4 as a spiral tube portion having an involute curve, and lids 6 and 6. The container 2, the partition wall 3, the spiral tube 4 and the lid 6 are all made of metal such as stainless steel or aluminum, and the spiral tube 4 is arranged in a plurality of stages inside the partition wall 3 and is in close contact by brazing. A partition wall 3 in which the spiral tubes 4 are in close contact with each other is arranged in the container 2, and the upper and lower openings of the container 2 are closed by lids 6 and 6.
　この場合、仕切壁３の上下端は蓋６、６の内面に密着してそれらの間が封止される。これにより、渦巻状の仕切壁３間には、渦巻の中心から回転しながら外側に向かう一連の渦巻通路７が構成される。渦巻管４はこの渦巻通路７内に位置して当該渦巻通路７内の空間と接するように配置される。これにより、渦巻管４は渦巻通路７内を流れる流体（後述する第一流体）と接することになる。また、複数段の渦巻管４は相互に間隔を存して配置されており、図２に示すように各渦巻管４の外側の端部（実施例では第二流体の入口側の端部）はヘッダ８で連通され、渦巻の中心側の端部（実施例では第二流体の出口側の端部）もヘッダ９で連通されている。 In this case, the upper and lower ends of the partition wall 3 are in close contact with the inner surfaces of the lids 6 and 6, and the space between them is sealed. As a result, a series of spiral passages 7 are formed between the spiral partition walls 3 toward the outside while rotating from the center of the spiral. The spiral tube 4 is disposed in the spiral passage 7 so as to be in contact with the space in the spiral passage 7. As a result, the spiral tube 4 comes into contact with a fluid (first fluid described later) flowing in the spiral passage 7. Further, the plurality of stages of the spiral tubes 4 are arranged with a space between each other, and as shown in FIG. 2, the outer end portions of the respective spiral tubes 4 (end portions on the inlet side of the second fluid in the embodiment). Is communicated with the header 8, and the end portion on the center side of the spiral (in the embodiment, the end portion on the outlet side of the second fluid) is also communicated with the header 9.
　そして、熱交換器１が例えばランキンサイクルにおける冷媒の凝縮器として使用される場合、渦巻通路７には渦巻の中心の近傍（中心部）の蓋６に形成された接続口１１から、第一流体としての例えば冷水が熱交換器１内に流入する。そして、渦巻通路７を図２中矢印で示すように渦巻の中心から外側に向けて反時計回りに回転しながら流れ、容器２の側面に形成された接続口１２から熱交換器１外に流出する。また、ヘッダ８からは第二流体としての例えば高温の冷媒が流入し、各渦巻管４内を図２中の外側から渦巻の中心に向けて時計回りに回転しながら流れ、ヘッダ９から熱交換器１外に流出する。 When the heat exchanger 1 is used, for example, as a refrigerant condenser in the Rankine cycle, the spiral passage 7 is connected to the first fluid from a connection port 11 formed in the lid 6 in the vicinity (center portion) of the center of the spiral. For example, cold water flows into the heat exchanger 1. Then, the spiral passage 7 flows while rotating counterclockwise from the center of the spiral toward the outside as indicated by an arrow in FIG. 2, and flows out of the heat exchanger 1 from the connection port 12 formed on the side surface of the container 2. To do. Further, for example, a high-temperature refrigerant as the second fluid flows from the header 8 and flows in each spiral tube 4 while rotating clockwise from the outside in FIG. 2 toward the center of the spiral, and heat exchange from the header 9 It flows out of the vessel 1.
　このとき、冷水（第一流体）の流れは図３中反時計回りとなり、冷媒（第二流体）の流れは逆に時計回りとなるので、冷水と冷媒の流れは全体としては相互に対向流となる。そのため、渦巻管４内を流れる冷媒と、その外側の渦巻通路７内を流れる水との温度差が冷媒（第二流体）の入口側となるヘッダ８から出口側のヘッダ９に渡る全範囲に渡って大きくなり、熱交換性能が向上する。特に、渦巻管４内を冷媒（第二流体）が流れるため、高圧冷媒が流れても高耐圧設計が容易となる。 At this time, the flow of the cold water (first fluid) is counterclockwise in FIG. 3, and the flow of the refrigerant (second fluid) is counterclockwise, so the flow of the cold water and the refrigerant is generally opposite to each other. It becomes. Therefore, the temperature difference between the refrigerant flowing in the spiral tube 4 and the water flowing in the spiral path 7 outside the entire range extends from the header 8 on the inlet side of the refrigerant (second fluid) to the header 9 on the outlet side. It increases over time, improving the heat exchange performance. In particular, since the refrigerant (second fluid) flows through the spiral tube 4, high pressure resistance design is facilitated even when a high-pressure refrigerant flows.
　この場合、渦巻の中心側のヘッダ９は、その外側に隣接する渦巻管４に当接しており、外側のヘッダ８は、外側に隣接する容器２と内側に隣接する仕切壁３の双方に当接している。尚、渦巻管４が仕切壁３の外側に密着される場合には、ヘッダ９はその外側に隣接する仕切壁３に当接し、ヘッダ８はその内側に隣接する渦巻管４に当接することになる。これにより、容器２の直径（胴径）Ｄ１は前述した図１４の従来例の熱交換器１００の容器１０２の直径（胴径）Ｄ２よりも小さくなる。 In this case, the header 9 on the center side of the spiral is in contact with the spiral tube 4 adjacent to the outside, and the outer header 8 contacts both the container 2 adjacent to the outside and the partition wall 3 adjacent to the inside. Touching. When the spiral tube 4 is in close contact with the outer side of the partition wall 3, the header 9 is in contact with the partition wall 3 adjacent to the outer side, and the header 8 is in contact with the spiral tube 4 adjacent to the inner side. Become. Thereby, the diameter (body diameter) D1 of the container 2 becomes smaller than the diameter (body diameter) D2 of the container 102 of the conventional heat exchanger 100 of FIG.
　また、実施例では仕切壁３はヘッダ８とヘッダ９の少許手前で終了しており、両ヘッダ８及びヘッダ９との間に間隔を構成している。これにより、ヘッダ８及びヘッダ９に接続される箇所の上下の渦巻管４の間には、内外の渦巻通路７を連通する連通部１３、１４が各ヘッダ８、９の近傍にそれぞれ形成されている（図３）。尚、連通部１３、１４の形状は、図３の実施形態に限定されることなく、例えば、仕切壁３の一部を切り欠いて形成することも可能である。 Further, in the embodiment, the partition wall 3 ends in front of the header 8 and the header 9 and a space is formed between the header 8 and the header 9. Thereby, between the upper and lower spiral tubes 4 connected to the header 8 and the header 9, communication portions 13 and 14 communicating the inner and outer spiral passages 7 are formed in the vicinity of the headers 8 and 9, respectively. (Fig. 3). In addition, the shape of the communication parts 13 and 14 is not limited to embodiment of FIG. 3, For example, a part of partition wall 3 can also be notched and formed.
　そして、渦巻通路７の渦巻の中心部に形成された接続口１１から冷水（第一流体）が熱交換器１内に流入する。渦巻の中心部には空間が形成されており、この空間に流入した冷水（第一流体）はヘッダ９の近傍に形成された連通部１４を通って外側の渦巻通路７に流出する。その後は渦巻通路７を図２中矢印で示すように渦巻の中心から外側に向けて反時計回りに回転しながら流れ、外側のヘッダ８の近傍に至る。 Then, cold water (first fluid) flows into the heat exchanger 1 from the connection port 11 formed at the center of the spiral of the spiral passage 7. A space is formed at the center of the spiral, and the cold water (first fluid) that has flowed into the space flows out to the outer spiral passage 7 through the communication portion 14 formed in the vicinity of the header 9. Thereafter, the spiral passage 7 flows while rotating counterclockwise from the center of the spiral toward the outside as indicated by an arrow in FIG. 2 and reaches the vicinity of the outer header 8.
　ヘッダ８の近傍まで流れて来た冷水（第一流体）は、当該ヘッダ８の近傍に形成された連通部１３を通って外側の容器２との間の空間に流出する。そして、今度は容器２と仕切壁３との間を時計回りに一周した後、容器２の側面の接続口１２から熱交換器１外に流出する。また、ヘッダ８からは高温の冷媒（第二流体）が流入し、各渦巻管４内を図２中時計回りに外側から渦巻の中心に向けて回転しながら流れ、ヘッダ９から熱交換器１外に流出する。冷水（第一流体）と冷媒（第二流体）とは対向流となるので、熱交換効率が高くなる。 The cold water (first fluid) flowing to the vicinity of the header 8 flows out to the space between the outer container 2 through the communication portion 13 formed in the vicinity of the header 8. Then, after making a round clockwise between the container 2 and the partition wall 3, it flows out of the heat exchanger 1 from the connection port 12 on the side surface of the container 2. Further, a high-temperature refrigerant (second fluid) flows from the header 8 and flows in each spiral tube 4 while rotating clockwise from the outside toward the center of the spiral in FIG. It flows out. Since the cold water (first fluid) and the refrigerant (second fluid) are opposed to each other, the heat exchange efficiency is increased.
　このように、渦巻管４の冷媒の入口側と出口側の端部に設けられたヘッダ８、９を備え、各ヘッダ８、９の近傍に、内外の渦巻通路７を連通する連通部１３、１４をそれぞれ形成したので、渦巻の中心部と容器２の側面との間で渦巻通路７内を流通する冷水（第一流体）が、ヘッダ８、９近傍の連通部１３、１４を経て内側と外側の渦巻通路７間を流れることができるようになる。 As described above, the headers 8 and 9 provided at the refrigerant inlet side and outlet end portions of the spiral tube 4 are provided, and in the vicinity of each of the headers 8 and 9, a communication portion 13 that communicates the inner and outer spiral passages 7, 14 is formed, so that the cold water (first fluid) flowing in the spiral passage 7 between the central portion of the spiral and the side surface of the container 2 passes through the communication portions 13 and 14 in the vicinity of the headers 8 and 9 and It becomes possible to flow between the outer spiral passages 7.
　これにより、実施例のように渦巻の中心側に位置するヘッダ９を、隣接する渦巻管４（若しくは仕切壁３）に当接させ、渦巻の外側に位置するヘッダ８を、隣接する容器２と、仕切壁３（若しくは渦巻管４）の双方に当接させたとしても、冷水（第一流体）は支障無くヘッダ８、９近傍の連通部１３、１４から内外の渦巻通路７間を流れることができるようになり、容器２の直径（胴径）Ｄ１を縮小して熱交換器１の小型化による重量の低減とコストの削減を図ることができるようになる。 Thereby, the header 9 located in the center side of the spiral is brought into contact with the adjacent spiral tube 4 (or the partition wall 3) as in the embodiment, and the header 8 positioned outside the spiral is connected to the adjacent container 2. Even if the partition wall 3 (or the spiral tube 4) is brought into contact with each other, the cold water (first fluid) flows between the communication portions 13 and 14 near the headers 8 and 9 between the inner and outer spiral passages 7 without any trouble. As a result, the diameter (body diameter) D1 of the container 2 can be reduced to reduce the weight and the cost by downsizing the heat exchanger 1.
　次に、図４は他の実施例の熱交換器１内部の平面図を示している。この実施例は、上述した実施例における仕切壁３及び渦巻管４に相当する仕切壁部３Ａ及び渦巻管部４Ａを、アルミニウム等の金属の押出成形により、押出材１５に一体に構成した例である。実施例の押出材１５には、内部に断面円形の流路を有する渦巻管部４Ａが上下複数段形成されており、各渦巻管部４Ａがそれらの間に位置する仕切壁部３Ａにより相互に接続された構成とされている。 Next, FIG. 4 shows a plan view of the inside of the heat exchanger 1 of another embodiment. This embodiment is an example in which the partition wall portion 3A and the spiral tube portion 4A corresponding to the partition wall 3 and the spiral tube 4 in the above-described embodiment are integrally formed with the extruded material 15 by extrusion molding of a metal such as aluminum. is there. The extruded material 15 of the embodiment is formed with a plurality of upper and lower spiral tube portions 4A having a circular passage in the inside, and each spiral tube portion 4A is mutually connected by a partition wall portion 3A located between them. Connected configuration.
　そして、この実施例の場合係る平板状の押出材１５をインボリュート曲線を成すように渦巻状に巻回することにより、内外の仕切壁部３Ａ及び渦巻管部４Ａの間に渦巻通路７を構成する。この場合も、渦巻の中心側のヘッダ９は、その外側に隣接する渦巻管部４Ａに当接しており、外側のヘッダ８は、外側に隣接する容器２と内側に隣接する渦巻管部４Ａの双方に当接している。 And the spiral channel | path 7 is comprised between the inner and outer partition wall part 3A and the spiral pipe part 4A by winding the flat extrusion material 15 which concerns on this Example in spiral shape so that an involute curve may be comprised. . Also in this case, the spiral-side header 9 is in contact with the spiral tube portion 4A adjacent to the outside, and the outer header 8 is formed between the container 2 adjacent to the outside and the spiral tube portion 4A adjacent to the inside. It is in contact with both sides.
　そしてこの場合は、ヘッダ８及び９の近傍の上下の渦巻管部４Ａ間の仕切壁部３Ａを削除することにより、連通部１３及び１４を形成している。これにより、前述の実施例同様に冷水（第一流体）の流れを確保しながら、熱交換器１の寸法の縮小を図ることができる。 In this case, the communication portions 13 and 14 are formed by deleting the partition wall portion 3A between the upper and lower spiral tube portions 4A in the vicinity of the headers 8 and 9. Thereby, the size of the heat exchanger 1 can be reduced while securing the flow of cold water (first fluid) as in the above-described embodiment.
　次に、図５は前述したようにインボリュート曲線を成す図４の仕切壁部３Ａ及び渦巻管部４Ａのヘッダ８、９の位置を規定する他の例を示している。この場合、インボリュート曲線の基礎円ＣＢに接する線Ｌ１が渦巻の外側に位置するヘッダ８の中心を通るようにしている。インボリュート曲線は、基礎円ＣＢ（リール）に巻き取られた糸（伸縮しない）を、基礎円ＣＢ自体は回転させずに真っ直ぐに引き張ってほどいていくときに、糸の端点が描く曲線であるが、線Ｌ１は基礎円ＣＢの糸をほどいていく側に接する（糸の上に載る）。 Next, FIG. 5 shows another example for defining the positions of the partition walls 3A and the spiral pipes 4A of the headers 8 and 9 in FIG. 4 forming the involute curve as described above. In this case, the line L1 in contact with the basic circle CB of the involute curve passes through the center of the header 8 located outside the spiral. The involute curve is a curve drawn by the end point of a thread when the thread wound around the base circle CB (reel) is stretched straight without rotating the base circle CB itself. However, the line L1 is in contact with the unwinding side of the basic circle CB (it is placed on the yarn).
　このように、渦巻の中心を挟んでヘッダ８の反対側位置する仕切壁部３Ａと容器２との間の間隔を確保しながら、容器２の直径（胴径）を最小とすることが可能となる。 In this way, it is possible to minimize the diameter (body diameter) of the container 2 while ensuring the space between the partition wall 3A located opposite to the header 8 and the container 2 across the center of the spiral. Become.
　尚、上記各実施例ではヘッダ８とヘッダ９の双方の近傍に連通部１３、１４を形成したが、何れか一方に形成してもよい。その場合には形成しない方のヘッダを渦巻管（渦巻管部）や仕切壁（仕切壁部）から離間させる必要が生じるが、図１４の場合よりも少なくとも容器の直径（胴径）を縮小できる。 In the above embodiments, the communication portions 13 and 14 are formed in the vicinity of both the header 8 and the header 9, but may be formed in either one. In that case, it is necessary to separate the header not formed from the spiral tube (vortex tube portion) or the partition wall (partition wall portion), but at least the diameter (body diameter) of the container can be reduced as compared with the case of FIG. .
　次に、図６～図８は冷媒（第二流体）が流れる渦巻管４（渦巻管部４Ａ）をパス割する例を示している。尚、図６～図８は熱交換器１を蒸発器として使用し、第二流体である冷媒を渦巻管４（渦巻管部４Ａ）内で第一流体である水（温水）と熱交換させて蒸発させるものである。そして、水（第一流体）は今度は外側の接続口１２から渦巻通路７内に流入し、渦巻の中心側の接続口１１から流出する。また、冷媒は（第二流体）は渦巻の中心側のヘッダ９の下部から流入し、外側のヘッダ８の上部から流出するものとする。 Next, FIGS. 6 to 8 show an example in which the spiral tube 4 (vortex tube portion 4A) through which the refrigerant (second fluid) flows is divided. 6 to 8 use the heat exchanger 1 as an evaporator to exchange heat between the coolant as the second fluid and the water (hot water) as the first fluid in the spiral tube 4 (vortex tube portion 4A). Evaporate. The water (first fluid) then flows into the spiral passage 7 from the outer connection port 12 and flows out from the connection port 11 on the center side of the spiral. The refrigerant (second fluid) flows in from the lower part of the header 9 on the spiral side and flows out from the upper part of the outer header 8.
　上記各実施例のように凝縮器として使用する場合も同様であるが、この場合のように蒸発器として使用し、例えば第一流体を水（この場合温水）、第二流体を冷媒とするとき、第一流体と第二流体の流量差が大きく、第一流体の流量＞第二流体の流量となる。このとき、第二流体の低流速や偏流による性能低下を防ぐには、第二流体のみパス割を行うことで、流路面積を減らし、流速を上げることが有効となる。 The same applies to the case of use as a condenser as in each of the above embodiments. However, in this case, for example, when the first fluid is water (in this case, warm water) and the second fluid is a refrigerant. The flow rate difference between the first fluid and the second fluid is large, and the flow rate of the first fluid> the flow rate of the second fluid. At this time, in order to prevent the performance deterioration due to the low flow velocity or the drift of the second fluid, it is effective to reduce the flow path area and increase the flow velocity by performing the pass division only for the second fluid.
　この場合、熱交換器の単位時間当たりの熱交換量Ｑは、式（１）で得られる。
　Ｑ［Ｗ］＝Ｕ［Ｗ／ｍ2・Ｋ］×Ａ［ｍ2］×ΔＴ［℃］　・・・（１）
　ここで、Ｕは総括伝熱係数、Ａは伝熱面積、ΔＴは第一流体と第二流体の有効温度差である。 In this case, the heat exchange amount Q per unit time of the heat exchanger is obtained by Expression (1).
Q [W] = U [W / m 2 · K] × A [m 2 ] × ΔT [° C.] (1)
Here, U is the overall heat transfer coefficient, A is the heat transfer area, and ΔT is the effective temperature difference between the first fluid and the second fluid.
　そして、有効温度差ΔＴは式（２）で表され、並流よりも対向流の方が大きな値となり、並流よりも対向流の方が、熱交換量Ｑは大となる。
　有効温度差ΔＴ＝対数平均温度差＝（ΔＴ１－ΔＴ２）／ｌｎ（ΔＴ１／ΔＴ２）・・・（２） The effective temperature difference ΔT is expressed by the equation (2). The counter flow has a larger value than the parallel flow, and the counter flow has a larger heat exchange amount Q than the parallel flow.
Effective temperature difference ΔT = Logarithm average temperature difference = (ΔT1−ΔT2) / ln (ΔT1 / ΔT2) (2)
　一方、前述のような理由で複数の渦巻管４（渦巻管部４Ａ）を、第二流体が往復して流れる複数のパスに分けた場合、何れかのパスは必ず第一流体と並流となり、有効温度差ΔＴの低下による性能低下が発生する。また、第二流体の下流側のパスにおいては、入口の第二流体（冷媒）の温度が高くなり、有効温度差ΔＴが低下する。 On the other hand, when the plurality of spiral tubes 4 (vortex tube portion 4A) are divided into a plurality of paths through which the second fluid reciprocates for the reasons described above, any of the paths is always in parallel with the first fluid. As a result, a decrease in performance occurs due to a decrease in effective temperature difference ΔT. Further, in the downstream path of the second fluid, the temperature of the inlet second fluid (refrigerant) increases, and the effective temperature difference ΔT decreases.
　そこで、この実施例では図６に示すように複数の渦巻管４を下から三つのパスＰＳ１、ＰＳ２、ＰＳ３に分ける。そして、渦巻管４の数はパスＰＳ１＜パスＰＳ２＜パスＰＳ３とし、且つ、パスＰＳ１が最上流、次にパスＰＳ２、そして、パスＰＳ３が最下流となるようにヘッダ８、９内を仕切１６で仕切る。 Therefore, in this embodiment, as shown in FIG. 6, the plurality of spiral tubes 4 are divided into three paths PS1, PS2, and PS3 from the bottom. The number of spiral tubes 4 is such that the path PS1 <the path PS2 <the path PS3, and the headers 8 and 9 are partitioned 16 so that the path PS1 is the most upstream, then the path PS2, and the path PS3 is the most downstream. Partition with.
　各図において太線矢印は第二流体である冷媒の流れを、白抜き矢印は第一流体である水（温水）の流れを示す。渦巻の中心側のヘッダ９の下部から流入した冷媒は最下部で最上流のパスＰＳ１に入り、パスＰＳ１を構成する渦巻管４内をヘッダ８に向かって流れ（往路）、次にヘッダ８から一つ上のパスＰＳ２に入り、パスＰＳ２を構成する渦巻４内をヘッダ９に向かって流れ（復路）、ヘッダ９から最上部で最下流のパスＰＳ３に入り、パスＰＳ３を構成する渦巻管４内をヘッダ８に向かって流れて流出する（往路）。従って、パスＰＳ１の第二流体は第一流体に対して対向流、パスＰＳ２では並流、パスＰＳ３では対向流となる。 In each figure, the bold arrow indicates the flow of the refrigerant that is the second fluid, and the white arrow indicates the flow of the water (hot water) that is the first fluid. The refrigerant flowing in from the lower part of the header 9 on the center side of the spiral enters the uppermost path PS1 at the lowermost part, flows in the spiral pipe 4 constituting the path PS1 toward the header 8 (forward path), and then from the header 8 Enters the path PS2 that is one level above, flows in the spiral 4 constituting the path PS2 toward the header 9 (return path), enters the path PS3 that is the most downstream from the header 9, and constitutes the path PS3. It flows toward the header 8 and flows out (outward path). Therefore, the second fluid in the path PS1 is a counterflow with respect to the first fluid, a parallel flow is in the path PS2, and a counterflow is in the path PS3.
　図７は各パスでの冷媒（第二流体）の状態を示している。ヘッダ９からパスＰＳ１に流入した冷媒は液相であり、ヘッダ８に向かうに従って徐々に蒸発していき、気液二相となる。そして、パスＰＳ２を流れる過程で更に蒸発するものの、気液二相の状態でパスＰＳ２をヘッダ９まで流れ、パスＰＳ３でヘッダ８に流れる過程で更に蒸発して気液二相から全て気相に変化する。 FIG. 7 shows the state of the refrigerant (second fluid) in each pass. The refrigerant flowing into the path PS1 from the header 9 is in a liquid phase, gradually evaporates toward the header 8, and becomes a gas-liquid two phase. Although it further evaporates in the process of flowing through the path PS2, it passes through the path PS2 to the header 9 in a gas-liquid two-phase state, and further evaporates in the process of flowing to the header 8 in the path PS3, so that all of the gas-liquid two-phase is changed into the gas phase Change.
　このように、渦巻管４を第二流体が往復して流れる三つのパスＰＳ１～ＰＳ３に分け、最も下流のパスＰＳ３を流れる第二流体が第一流体に対して対向流となるように構成している。そして、最下流のパスＰＳ３の渦巻管４の数を他のパスよりも多くしているので、実施例のように熱交換器１を蒸発器として使用し、第二流体を冷媒として第一流体（温水）との熱交換で蒸発させるときには、最も渦巻管４の数が多く伝熱面積が最大となる最下流のパスＰＳ３が、熱交換性能が高まる対向流となり、熱交換器１の熱交換性能の向上を図ることが可能となる。 In this way, the spiral tube 4 is divided into three paths PS1 to PS3 through which the second fluid reciprocates, and the second fluid flowing through the most downstream path PS3 is configured to face the first fluid. ing. Since the number of the spiral tubes 4 in the most downstream path PS3 is larger than that in the other paths, the heat exchanger 1 is used as an evaporator as in the embodiment, and the second fluid is used as a refrigerant and the first fluid. When evaporating by heat exchange with (warm water), the most downstream path PS3 having the largest number of spiral tubes 4 and the largest heat transfer area becomes a counter flow with improved heat exchange performance, and heat exchange of the heat exchanger 1 is performed. The performance can be improved.
　また、最下流よりも上流のパスＰＳ２では冷媒（第二流体）は気液二相となり、温度が一定となるので、第一流体（温水）と並流となっても対向流の場合と変わらなくなり、熱交換性能の低下を防止できる。更に、気液二相のパスＰＳ２では下流ほど気相の占める割合が高まり、流速が増すことで熱伝達率が向上する。従って、並流となることによる熱交換性能の低下を、熱伝達率の向上により補い、性能の改善を図ることができる。 Further, in the path PS2 upstream from the most downstream, the refrigerant (second fluid) is in a gas-liquid two-phase and the temperature is constant, so that even if it is in parallel flow with the first fluid (warm water), it is different from the counterflow case. It is possible to prevent a decrease in heat exchange performance. Furthermore, in the gas-liquid two-phase path PS2, the proportion of the gas phase increases toward the downstream, and the heat transfer rate is improved by increasing the flow velocity. Therefore, the deterioration of the heat exchange performance due to the parallel flow can be compensated for by improving the heat transfer coefficient, and the performance can be improved.
　ここで、図８は図６、図７の例における各部における冷媒（第二流体）の温度を示している。冷媒はヘッダ９から最下部のパスＰＳ１を構成する渦巻管４に流入した時点では例えば＋４０℃であったものがヘッダ８に至る時点では温水（例えば＋９５℃）との熱交換により＋８２℃まで上昇し、パスＰＳ２では温度は変わらず、最上部のパスＰＳ３でヘッダ８に至る時点では更に８７℃まで上昇する。 Here, FIG. 8 shows the temperature of the refrigerant (second fluid) in each part in the examples of FIGS. When the refrigerant flows into the spiral tube 4 constituting the lowermost path PS1 from the header 9, for example, the temperature is + 40 ° C., but when the refrigerant reaches the header 8, it rises to + 82 ° C. by heat exchange with warm water (for example, + 95 ° C.). However, the temperature does not change in the path PS2, and further rises to 87 ° C. when reaching the header 8 in the uppermost path PS3.
　このように、最上部のパスＰＳ３では温水（第一流体）と冷媒（第二流体）との温度差が小さくなるため、下流側（螺旋の中心側）における温水の温度は、熱交換器１の下部では低いが、上部で高くなり、熱が利用されないまま流出することになる。 Thus, in the uppermost path PS3, the temperature difference between the hot water (first fluid) and the refrigerant (second fluid) becomes small, so the temperature of the hot water on the downstream side (center side of the spiral) is the heat exchanger 1. It is low in the lower part of the water, but higher in the upper part, and the heat flows out without being used.
　そこで、図９に示すように冷媒（第二流体）の入口側となるヘッダ９の上流側にプリヒータ１７を取り付け、プリヒータ１７を下流側の温水（第一流体）と下部から上部に渡って熱交換できるように配置し、冷媒はこのプリヒータ１７を流れた後、ヘッダ９に流入するようにする。 Therefore, as shown in FIG. 9, a preheater 17 is attached to the upstream side of the header 9 serving as the refrigerant (second fluid) inlet side, and the preheater 17 is heated from the lower side to the hot water (first fluid) and from the lower part to the upper part. It arrange | positions so that replacement | exchange is possible, and after a refrigerant | coolant flows through this preheater 17, it flows in into the header 9. FIG.
　このように、冷媒（第二流体）の入口側のヘッダ９の上流側にプリヒータ１７を取り付け、このプリヒータ１７と下流側の温水（第一流体）とを熱交換させるようにすれば、熱交換器１の渦巻管４に流入する前の冷媒（第二流体）と、この温度の高い上部の温水（第一流体）と熱交換させて第一流体の熱を有効に利用することができるようになる。 As described above, if the preheater 17 is attached to the upstream side of the header 9 on the inlet side of the refrigerant (second fluid) and heat is exchanged between the preheater 17 and the hot water (first fluid) on the downstream side, heat exchange is performed. It is possible to effectively use the heat of the first fluid by exchanging heat with the refrigerant (second fluid) before flowing into the spiral tube 4 of the vessel 1 and the hot water (first fluid) at the upper part of this temperature. become.
　図１０はプリヒータ１７の熱交換器１への配置例を示している。この例では仕切壁３及び渦巻管４の渦巻の中心に形成される容器２内の空間に配置する。この空間は温水（第一流体）の下流側となる。これにより、渦巻の中心部にどうしても形成されてしまう容器２内の空間を利用してプリヒータ１７を設け、容器２の寸法の拡大を防止することができるようになる。 FIG. 10 shows an arrangement example of the preheater 17 on the heat exchanger 1. In this example, the partition wall 3 and the spiral tube 4 are arranged in a space in the container 2 formed at the center of the spiral. This space is downstream of the hot water (first fluid). Thereby, the preheater 17 is provided using the space in the container 2 that is inevitably formed at the center of the spiral, and the expansion of the dimensions of the container 2 can be prevented.
　尚、図１１、図１２はこのプリヒータ１７の構成例を示している。図１１はプリヒータ１７を螺旋状の配管で構成した場合、図１２は無数の突起１８を取り付けた配管でプリヒータ１７を構成した場合を示している。何れの場合にも、渦巻管４に流入する前の冷媒（第二流体）と温水（第一流体）とを十分に熱交換させることができる。 11 and 12 show an example of the configuration of the preheater 17. FIG. 11 shows a case where the preheater 17 is constituted by a spiral pipe, and FIG. 12 shows a case where the preheater 17 is constituted by a pipe having innumerable protrusions 18 attached thereto. In any case, it is possible to sufficiently exchange heat between the refrigerant (second fluid) and the hot water (first fluid) before flowing into the spiral tube 4.
　また、上記実施例によらず、図２の場合と同様に第一流体（この場合は蒸発器であるから温水）が渦巻の中心側から流入し、容器２側から流出する場合には、渦巻の外側に位置するヘッダ８が冷媒の入口側となるので、プリヒータ１７を渦巻の外側に位置するヘッダ８近傍に形成される容器２内の空間（図２中に破線の円で囲んだ空間ＳＸ）に配置する。これにより、外側のヘッダ近傍にどうしても形成されてしまう容器内空間を利用してプリヒータを設け、寸法の拡大を防止することができるようになる。 Further, regardless of the above embodiment, when the first fluid (in this case, warm water because it is an evaporator) flows in from the center side of the spiral and flows out from the container 2 side as in the case of FIG. Since the header 8 located outside the refrigerant becomes the refrigerant inlet side, the space in the container 2 formed in the vicinity of the header 8 located outside the vortex of the preheater 17 (the space SX surrounded by a broken circle in FIG. 2) ). As a result, the preheater can be provided using the space inside the container that is inevitably formed near the outer header, and the size can be prevented from increasing.
　また、図１３は熱交換器１を図２の場合のように凝縮器として使用する場合のパス割を示している。この場合は、複数の渦巻管４を上から二つのパスＰＳ４、ＰＳ５に分ける。そして、渦巻管４の数はパスＰＳ５＜パスＰＳ４とし、且つ、パスＰＳ４が上流、パスＰＳ５が下流となるようにヘッダ８、９内を仕切１６で仕切る。 FIG. 13 shows a pass ratio when the heat exchanger 1 is used as a condenser as in FIG. In this case, the plurality of spiral tubes 4 are divided into two paths PS4 and PS5 from the top. Then, the number of spiral tubes 4 is such that path PS5 <path PS4, and the headers 8 and 9 are partitioned by a partition 16 so that the path PS4 is upstream and the path PS5 is downstream.
　この図においても太線矢印は第二流体である冷媒の流れを、白抜き矢印は第一流体である水（この場合は冷水）の流れを示す。渦巻の中心側のヘッダ９の上部から流入した冷媒は上部で上流のパスＰＳ４に入り、パスＰＳ４を構成する渦巻管４内をヘッダ８に向かって流れ（往路）、次にヘッダ８から下のパスＰＳ５に入り、パスＰＳ５を構成する渦巻４内をヘッダ９に向かって流れて流出する（復路）。従って、パスＰＳ４の第二流体は第一流体に対して並流、パスＰＳ５では対向流となる。 Also in this figure, the bold arrow indicates the flow of the refrigerant that is the second fluid, and the white arrow indicates the flow of the water that is the first fluid (in this case, cold water). The refrigerant flowing in from the upper part of the header 9 at the center of the spiral enters the upstream path PS4 at the upper part, flows in the spiral pipe 4 constituting the path PS4 toward the header 8 (forward path), and then flows downward from the header 8 It enters the path PS5, flows through the spiral 4 constituting the path PS5 toward the header 9, and flows out (return path). Therefore, the second fluid in the path PS4 becomes a parallel flow with respect to the first fluid, and becomes an opposite flow in the path PS5.
　ヘッダ９からパスＰＳ４に流入した冷媒は気相（温度は＋６５℃）であり、ヘッダ８に向かうに従って＋１５℃程の冷水（第一流体）で徐々に凝縮していき、気液二相となる。そして、パスＰＳ５を流れる過程で更に凝縮してヘッダ９に戻る時点では液リッチの気液二相となる。 The refrigerant flowing into the path PS4 from the header 9 is in a gas phase (temperature is + 65 ° C.), and gradually condenses with cold water (first fluid) of about + 15 ° C. toward the header 8 to become a gas-liquid two phase. . And at the time of further condensing in the process of flowing through the path PS5 and returning to the header 9, it becomes a liquid-rich gas-liquid two phase.
　このように、熱交換器１を凝縮器として使用し、冷媒（第二流体）を冷水（第一流体）との熱交換で凝縮させる場合にも、冷媒（第二流体）が熱伝達率の低い気相において、冷水（第一流体）との最大の温度差を確保することができ、上流側のパスＰＳ４が並流となっても熱交換性能を向上させることが可能となる。 Thus, even when the heat exchanger 1 is used as a condenser and the refrigerant (second fluid) is condensed by heat exchange with cold water (first fluid), the refrigerant (second fluid) has a heat transfer coefficient. In the low gas phase, the maximum temperature difference with the cold water (first fluid) can be secured, and the heat exchange performance can be improved even if the upstream path PS4 becomes a parallel flow.
　尚、実施例ではランキンサイクルで水（冷水や温水）と冷媒との熱交換を実現する熱交換器を例に説明したが、それに限らず、あらゆる用途の渦巻型の熱交換器に本発明は有効である。また、実施例では第一流体を水（冷水や温水）、第二流体を冷媒としたが、それに限らず、温度差のある種々の流体相互の熱交換に本発明の熱交換器は利用可能である。 In addition, although the Example demonstrated the heat exchanger which implement | achieves heat exchange with water (cold water and warm water) and a refrigerant | coolant by Rankine cycle as an example, it is not restricted to this, The present invention is applied to the spiral heat exchanger of all uses. It is valid. In the embodiments, the first fluid is water (cold water or hot water) and the second fluid is a refrigerant. However, the heat exchanger of the present invention can be used for heat exchange between various fluids having temperature differences. It is.
　１　熱交換器
　２　容器
　３　仕切壁（仕切壁部）
　３Ａ　仕切壁部
　４　渦巻管（渦巻管部）
　４Ａ　渦巻管部
　６　蓋
　７　渦巻通路
　８、９　ヘッダ
　１１、１２　接続口
　１３、１４　連通部
　１７　プリヒータ 1 Heat exchanger 2 Container 3 Partition wall (partition wall)
3A Partition wall 4 Swirl tube (Swirl tube)
4A spiral tube portion 6 lid 7 spiral passage 8, 9 header 11, 12 connection port 13, 14 communication portion 17 preheater

Claims (11)

  1. 　容器内に設けられた渦巻状の仕切壁部間に渦巻通路を構成し、該渦巻通路に接する渦巻管部を上下複数段設けて該渦巻管部外側の前記渦巻通路内を流れる第一流体と前記渦巻管部内を流れる第二流体とを熱交換させる熱交換器において、
    　前記渦巻管部の端部に設けられたヘッダを備え、該ヘッダ近傍に、内外の前記渦巻通路を連通する連通部を形成したことを特徴とする熱交換器。     A first fluid flowing in the spiral passage outside the spiral tube portion by forming a spiral passage between the spiral partition walls provided in the container, and providing a plurality of upper and lower spiral tube portions in contact with the spiral passage; In the heat exchanger for exchanging heat with the second fluid flowing in the spiral tube part,
    A heat exchanger comprising a header provided at an end of the spiral tube portion, and a communication portion that communicates the internal and external spiral passages in the vicinity of the header.
  2. 　前記ヘッダは、前記渦巻管部の前記第二流体の入口側と出口側の端部にそれぞれ設けられ、前記連通部は前記各ヘッダのうちの何れか一方、若しくは、双方の近傍に形成されていることを特徴とする請求項１に記載の熱交換器。 The header is provided at each end of the second fluid inlet side and outlet side of the spiral tube part, and the communication part is formed in either one of the headers or in the vicinity thereof. The heat exchanger according to claim 1, wherein:
  3. 　前記仕切壁部を構成する仕切壁と、前記渦巻管部を構成する渦巻管とを備え、該渦巻管が前記仕切壁に密着して設けられると共に、前記仕切壁を前記ヘッダの近傍で終了させることにより、前記連通部が形成されていることを特徴とする請求項１又は請求項２に記載の熱交換器。 A partition wall constituting the partition wall portion and a spiral tube constituting the spiral tube portion, the spiral tube being provided in close contact with the partition wall and terminating the partition wall in the vicinity of the header The heat exchanger according to claim 1, wherein the communication portion is formed.
  4. 　前記仕切壁部と前記渦巻管部は一体に押出成形されており、前記連通部は前記渦巻管部以外の部分の前記仕切壁部を削除して形成されていることを特徴とする請求項１又は請求項２に記載の熱交換器。 2. The partition wall portion and the spiral tube portion are integrally formed by extrusion, and the communication portion is formed by deleting the partition wall portion of a portion other than the spiral tube portion. Or the heat exchanger of Claim 2.
  5. 　渦巻の中心側に位置する前記ヘッダを、隣接する前記仕切壁部若しくは渦巻管部に当接させ、及び／又は、渦巻の外側に位置する前記ヘッダを、隣接する前記容器と、前記仕切壁部若しくは前記渦巻管部の双方に当接させたことを特徴とする請求項１乃至請求項４のうちの何れかに記載の熱交換器。 The header located on the center side of the spiral is brought into contact with the adjacent partition wall or spiral tube, and / or the header positioned outside the spiral is placed on the adjacent container and the partition wall. Or it is made to contact | abut both of the said spiral tube parts, The heat exchanger in any one of the Claims 1 thru | or 4 characterized by the above-mentioned.
  6. 　前記仕切壁部及び渦巻管部はインボリュート曲線を成し、該インボリュート曲線の基礎円に接する線が前記渦巻の外側に位置するヘッダの中心を通るようにしたことを特徴とする請求項５に記載の熱交換器。 6. The partition wall portion and the spiral tube portion form an involute curve, and a line in contact with a basic circle of the involute curve passes through the center of a header located outside the spiral. Heat exchanger.
  7. 　前記渦巻管部は前記第二流体が往復して流れる複数のパスに分けられ、最も下流のパスを流れる前記第二流体が前記第一流体に対して対向流となるように構成したことを特徴とする請求項１乃至請求項６のうちの何れかに記載の熱交換器。 The spiral tube section is divided into a plurality of paths through which the second fluid reciprocates, and the second fluid flowing in the most downstream path is configured to be opposed to the first fluid. The heat exchanger according to any one of claims 1 to 6.
  8. 　前記第二流体を蒸発させるものであり、前記最も下流のパスを構成する前記渦巻管部の数を他のパスより多くしたことを特徴とする請求項７に記載の熱交換器。 The heat exchanger according to claim 7, wherein the second fluid is evaporated, and the number of the spiral tube portions constituting the most downstream path is larger than that of other paths.
  9. 　前記第二流体の入口側の前記ヘッダの上流側にプリヒータを取り付け、該プリヒータと下流側の前記第一流体とを熱交換させることを特徴とする請求項８に記載の熱交換器。 The heat exchanger according to claim 8, wherein a preheater is attached to the upstream side of the header on the inlet side of the second fluid, and heat exchange is performed between the preheater and the first fluid on the downstream side.
  10. 　前記第一流体を前記渦巻の中心から流出させると共に、前記プリヒータを前記渦巻の中心に形成される前記容器内空間に配置したことを特徴とする請求項９に記載の熱交換器。 The heat exchanger according to claim 9, wherein the first fluid is allowed to flow out from the center of the spiral and the preheater is disposed in the inner space of the container formed at the center of the spiral.
  11. 　前記第一流体を前記渦巻の中心から流入させると共に、前記プリヒータを渦巻の外側に位置する前記ヘッダ近傍に形成される前記容器内空間に配置したことを特徴とする請求項９に記載の熱交換器。 10. The heat exchange according to claim 9, wherein the first fluid is caused to flow from the center of the spiral and the preheater is disposed in the inner space of the container formed in the vicinity of the header located outside the spiral. vessel.
PCT/JP2014/070607 2013-08-08 2014-08-05 Heat exchanger WO2015020048A1 (en)

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CN112437594A (en) * 2020-11-26 2021-03-02 北京石油化工学院 Vortex-shaped micro-channel heat exchanger

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JP7170011B2 (en) * 2020-08-31 2022-11-11 ジオシステム株式会社 heat exchanger
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JPS57178978U (en) * 1981-04-28 1982-11-12
JP2002153931A (en) * 2000-11-21 2002-05-28 Mitsubishi Heavy Ind Ltd Heat exchange tube and finless heat exchanger
JP2004037020A (en) * 2002-07-04 2004-02-05 Honda Motor Co Ltd Heat exchanger and heat exchange type reactor using the same
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JP2012180982A (en) * 2011-03-02 2012-09-20 Panasonic Corp Heat exchanger, and heat pump water heater using the same

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WO2019101568A1 (en) 2017-11-23 2019-05-31 Basf Se Method for producing bispyrrolidine compounds
US11345680B2 (en) 2017-11-23 2022-05-31 Basf Se Method for producing bispyrrolidine compounds
CN112437594A (en) * 2020-11-26 2021-03-02 北京石油化工学院 Vortex-shaped micro-channel heat exchanger

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