EP3495760A1 - Wärmetauscher und kältekreislaufvorrichtung mit dem wärmetauscher - Google Patents

Wärmetauscher und kältekreislaufvorrichtung mit dem wärmetauscher Download PDF

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Publication number
EP3495760A1
EP3495760A1 EP16911650.6A EP16911650A EP3495760A1 EP 3495760 A1 EP3495760 A1 EP 3495760A1 EP 16911650 A EP16911650 A EP 16911650A EP 3495760 A1 EP3495760 A1 EP 3495760A1
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EP
European Patent Office
Prior art keywords
pipe
heat medium
flow path
heat exchanger
region
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP16911650.6A
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English (en)
French (fr)
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EP3495760B1 (de
EP3495760A4 (de
Inventor
Kensaku HATANAKA
Toru Tonegawa
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication date
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Publication of EP3495760A1 publication Critical patent/EP3495760A1/de
Publication of EP3495760A4 publication Critical patent/EP3495760A4/de
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Publication of EP3495760B1 publication Critical patent/EP3495760B1/de
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Classifications

    • 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
    • F28D7/0008—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 for one medium being in heat conductive contact with the conduits for the other medium
    • F28D7/0016—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 for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being bent
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/18—Water-storage heaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H4/00—Fluid heaters characterised by the use of heat pumps
    • F24H4/02—Water heaters
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/02—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/06—Heat exchange conduits having walls comprising obliquely extending corrugations, e.g. in the form of threads

Definitions

  • the present invention relates to a heat exchanger and a refrigeration cycle apparatus including the heat exchanger, and more particularly, to a heat exchanger having a structure in which a pipe through which refrigerant flows is wound around a pipe through which water or another heat medium flows.
  • a gas cooler of a heat-pump water heating apparatus proposed is a gas cooler including a first pipe (core pipe), in which a flow path through which a heat medium (water) flows is formed, and a second pipe (outer pipe) through which refrigerant flows, and is wound around an outer periphery of the first pipe (see, for example, Patent Literature 1).
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. 2008-249163
  • a distribution of a flow velocity of water in the first pipe varies depending on the shape of the first pipe.
  • a flow velocity of water passing through an inner peripheral surface side of the first pipe is lower than a flow velocity of water passing through a diameter center of the first pipe.
  • the flow of the water passing through the inner peripheral surface side of the first pipe tends to stagnate, and hence the temperature of the water rises as compared with the water passing through the diameter center of the first pipe. That is, in the water passing through the inner peripheral surface side of the first pipe, the amount of heat received from the refrigerant flowing through the second pipe tends to increase.
  • a structure including irregularities is often formed in the first pipe. That is, the flow of the water passing through the inner peripheral surface side of the first pipe tends to stagnate, while in a part having such a structure formed therein, the flow of the water further tends to stagnate and the water temperature tends to increase. For this reason, scale contained in water tends to be precipitated in the part having such a structure. This is because a solubility of the scale in water decreases as the water temperature increases, and the scale is precipitated without being dissolved in water in a part in which the water temperature tends to rise.
  • the present invention has been made in order to solve the above-mentioned problem, and an object thereof is to provide a heat exchanger capable of suppressing precipitation of scale in a pipe, as well as to provide a refrigeration cycle apparatus including the heat exchanger.
  • a heat exchanger including: a first pipe having a first flow path formed therein, the first flow path being configured to flow a heat medium therethrough, and a second pipe having a second flow path formed therein and being wound around the first pipe, the second flow path being configured to flow refrigerant therethrough, wherein the first pipe has an inflow port for the heat medium and an outflow port for the heat medium formed therein so that the inflow port and the outflow port communicate with the first flow path, wherein the first pipe includes: a crest portion, which protrudes in a diameter-increasing direction in which a diameter of the first pipe is increased; and a trough portion having an outer diameter smaller than an outer diameter of a part in which the crest portion is formed and around which the second pipe is wound, wherein the crest portion is formed in a helical shape in the first flow path in a direction in which the heat medium flows, wherein the trough portion is formed in a helical shape along the
  • the heat exchanger according to one embodiment of the present invention which has the above-mentioned configuration, can inhibit scale from being precipitated in the first pipe.
  • Fig. 1 is a diagram illustrating an example of a schematic configuration of a refrigeration cycle apparatus 100 including a heat exchanger 2 according to this embodiment. With reference to Fig. 1 , a description is given on a configuration of the refrigeration cycle apparatus 100.
  • the refrigeration cycle apparatus 100 includes a refrigerant circuit C1, a heat medium circuit C2, a controller Cnt, and different kinds of detection units 10A to 10D.
  • the refrigeration cycle apparatus 100 is also connected to a hot-water using unit U and a water supply circuit C3.
  • the hot-water using unit U corresponds to each of different kinds of components, for example, a water faucet and a bath unit in a home, which require hot water.
  • the water supply circuit C3 corresponds to a pipe for water supply or another component.
  • the refrigerant circuit C1 circulates refrigerant therethrough.
  • the refrigerant for example, a carbon dioxide refrigerant can be employed.
  • the refrigerant circuit C1 includes a compressor 1 configured to compress the refrigerant, a second flow path FP2 (see Fig. 2D ) of the heat exchanger 2 functioning as a condenser, an expansion device 3, and a heat exchanger 4 functioning as an evaporator.
  • the second flow path FP2 refers to one of flow paths of the heat exchanger 2 in which the refrigerant flows.
  • the heat exchanger 2 exchanges heat between the refrigerant flowing through the refrigerant circuit C1 and a heat medium passing therethrough to condense the refrigerant.
  • the heat exchanger 2 is a heat medium-refrigerant heat exchanger configured to exchange heat between the heat medium and the refrigerant.
  • the heat exchanger 2 is formed of a double pipe heat exchanger in which a first pipe 41 having the heat medium flowing therethrough and a second pipe 42 having the refrigerant flowing therethrough are brought into contact with each other.
  • the heat exchanger 4 can be formed of, for example, a fin-tube heat exchanger.
  • the heat medium circuit C2 circulates a heat medium therethrough.
  • the heat medium for example, water or an antifreeze solution can be employed.
  • the heat medium circuit C2 includes a first flow path FP1 (see Fig. 2D ) of the heat exchanger 2 and a pump 5 configured to convey the heat medium.
  • the first flow path FP1 refers to one of the flow paths of the heat exchanger 2 in which the heat medium flows.
  • the detection unit 10A is an outside air temperature detection sensor configured to detect an outside air temperature.
  • the detection unit 10B is a discharge refrigerant temperature detection sensor configured to detect a refrigerant temperature on a discharge side of the compressor 1.
  • the detection unit 10C is an inlet temperature detection sensor configured to detect a heat medium temperature at an inlet of the heat exchanger 2.
  • the detection unit 10D is an outlet temperature detection sensor configured to detect a heat medium temperature at an outlet of the heat exchanger 2.
  • a detection unit 10E is a flow rate detection sensor configured to detect a flow rate of the heat medium flowing through the heat medium circuit C2.
  • the controller Cnt controls the compressor 1, the expansion device 3, the pump 5, and other components based on detection results obtained by the detection units 10A to 10D.
  • scale contained in the heat medium is hard to be precipitated in the heat exchanger 2. Meanwhile, it is difficult to completely prevent the precipitation of the scale, and hence the refrigeration cycle apparatus 100 has a function of determining the precipitation of the scale in the heat exchanger 2.
  • the scale refers to a precipitate containing calcium carbonate as its main component.
  • Each functional unit included in the controller Cnt is formed of dedicated hardware or a micro processing unit (MPU) configured to execute a program stored in a memory.
  • MPU micro processing unit
  • the controller Cnt When the controller Cnt is formed of the dedicated hardware, the controller Cnt corresponds to, for example, a single circuit, a composite circuit, an application specific integrated circuit (ASIC), a field-programmable gate array (FPGA), or a combination of those circuits.
  • the functional units implemented by the controller Cnt may each be achieved by individual pieces of hardware, or a single piece of hardware may be used to achieve the functional units.
  • each function executed by the controller Cnt is achieved by software, firmware, or a combination of software and firmware.
  • the software or the firmware is described as a program and is stored in a memory.
  • the MPU is configured to read out and execute the program stored in the memory, to thereby achieve each of the functions of the controller Cnt.
  • the memory is, for example, a RAM, a ROM, a flash memory, an EPROM, an EEPROM, or other types of non-volatile or volatile semiconductor memory.
  • Fig. 2A is a perspective view of the heat exchanger 2 according to this embodiment.
  • Fig. 2B is an explanatory diagram of the first pipe 41 of the heat exchanger 2 according to this embodiment.
  • Fig. 2C is an explanatory diagram of the first pipe 41 of the heat exchanger 2 according to this embodiment and the second pipe 42 wound around the first pipe 41.
  • Fig. 2D is an enlarged view of a cross section of a part of the heat exchanger 2 according to this embodiment.
  • the heat exchanger 2 includes the first pipe 41, in which the first flow path FP1 through which the heat medium flows is formed, and the second pipe 42, in which the second flow path FP2 through which the refrigerant flows is formed, and the second pipe 42 is wound around the first pipe 41.
  • an inflow port 41a for the heat medium and an outflow port 41b for the heat medium are formed so as to communicate with the first flow path FP1.
  • an inflow port 42a for the refrigerant and an outflow port 42b for the refrigerant are formed so as to communicate with the second flow path FP2.
  • the heat exchanger 2 can be connected to the refrigerant circuit C1 and the heat medium circuit C2 so that, for example, a direction in which the heat medium flows through the first pipe 41 and a direction in which the refrigerant flows through the second pipe 42 face to each other. This improves heat exchange efficiency between the heat medium and the refrigerant.
  • the first pipe 41 includes a crest portion 41A, which protrudes in a diameter-increasing direction DR1 for increasing a diameter of the first pipe 41.
  • the crest portion 41A is formed in a helical shape in a direction of the first flow path FP1 in which the heat medium flows.
  • the crest portion 41A is formed in the first pipe 41 in a helical shape.
  • the diameter-increasing direction DR1 refers to a direction extending from an inner peripheral surface S1 side of the first pipe 41 to an outer peripheral surface S2 of the first pipe 41.
  • a trough portion 41B having an outer diameter smaller than that of a part in which the crest portion 41A is formed is formed.
  • the second pipe 42 is wound around the trough portion 41B.
  • the trough portion 41B is formed in a helical shape along the crest portion 41A. That is, the crest portion 41A and the trough portion 41B are formed in parallel with each other.
  • FIG. 2B A case of forming one thread by crest portion 41A in the first pipe 41 is now described as an example.
  • Fig. 2B in order to clarify the location of the crest portion 41A, four threads formed by crest portions 41A are illustrated on each of the top and bottom of the first pipe 41 for the sake of convenience of description.
  • a plurality of threads formed by crest portions 41A are not formed in the first pipe 41, but one thread formed by crest portion 41A is formed in the first pipe 41 so as to extend in a helical shape.
  • the crest portion 41A is formed so as to extend around the first pipe 41 a plurality of times.
  • the trough portion 41B is also formed so as to extend around the first pipe 41 a plurality of times.
  • the trough portion 41B is formed between the crest portion 41A in the N-th round and the crest portion 41A in the (N+1)th round.
  • the crest portion 41A is formed between the trough portion 41B in the N-th round and the crest portion 41A in the (N+1)th round.
  • N is a natural number.
  • the trough portion 41B includes a plurality of concave portions 41C, which are formed so as to be aligned with each other in a helical direction which is a direction in which the trough portion 41B is formed, and are recessed in a diameter-decreasing direction DR2 in which the diameter of the first pipe 41 is decreased.
  • the heat exchanger 2 has a structure in which the crest portion 41A and the trough portion 41B are formed, and a flow of the heat medium tends to stagnate particularly in a part of the crest portion 41A. That is, as illustrated in Fig. 2D , a stagnation portion T is formed in the heat exchanger 2.
  • the flow of the heat medium tends to stagnate and the flow velocity of the heat medium is slow.
  • the heat medium in the stagnation portion T is liable to cause a local temperature rise due to the stagnant flow.
  • a solubility of scale in the heat medium decreases as the temperature of the heat medium rises. Therefore, in the stagnation portion T, scale that can no longer be dissolved in the heat medium tends to be precipitated. If the scale precipitated in the pipe peels off, the pipe is caused to be clogged by the peeled-off scale.
  • the concave portions 41C are formed in the heat exchanger 2 according to this embodiment, and hence agitation of the heat medium in the stagnation portion T is promoted. That is, when the heat medium passes through the concave portion 41C, a vortex is formed at a position at which the concave portion 41C is formed. As a result, the heat medium flowing through a central side of the first pipe 41 and the heat medium flowing through the stagnation portion T side of the first pipe 41 are agitated. The agitation can suppress a local temperature rise in the stagnation portion T, and also can suppress precipitation of scale in the first pipe 41.
  • the first pipe 41 has a smaller inner diameter in a part having the concave portion 41C formed therein than in a part having the trough portion 41B formed therein. That is, in the part having the concave portion 41C formed therein, not only the outer peripheral surface S2 of the first pipe 41 is recessed, but also the inner peripheral surface S1 is recessed.
  • the first pipe 41 and the second pipe 42 can be joined together by, for example, soldering. This improves heat transfer efficiency between the refrigerant and the heat medium, and an effect of improving the strength of the heat exchanger 2 can be expected.
  • Fig. 2E is an explanatory diagram of a part on an outlet side for the heat medium of the first pipe 41 of the heat exchanger 2 according to this embodiment.
  • Fig. 2F is an explanatory diagram of a part on an inlet side for the heat medium of the first pipe 41 of the heat exchanger 2 according to this embodiment.
  • the first pipe 41 is configured such that more concave portions 41C are distributed on the outflow port 41b side than on the inflow port 41a side. This configuration is designed by taking into consideration the fact that the temperature of the heat medium flowing through the first flow path FP1 rises as the heat medium flows from the inflow port 41a toward the outflow port 41b side, which is liable to cause the local temperature rise of the heat medium in the stagnation portion T.
  • the first pipe 41 has the following configuration.
  • a part of the first pipe 41 on the inflow port 41a side is set as a first region Rg1, and a part of the first pipe 41 on the outflow port 41b side is set as a second region Rg2 (see Fig. 3C ).
  • the concave portions 41C have a larger total area per unit length in the second region Rg2 than a total area per unit length in the first region Rg1.
  • This configuration which has a mode of forming a plurality of concave portions 41C in spot-like shapes, can be paraphrased as follows. That is, the concave portions 41C are distributed so that the number of concave portions 41C formed per unit length in the second region Rg2 is larger than the number of concave portions 41C formed per unit length in the first region Rg1.
  • Fig. 2G is an explanatory diagram of a flow velocity distribution of the heat medium in the first pipe in which no concave portions 41C are formed.
  • Fig. 2H is an explanatory diagram of a flow velocity distribution of the heat medium in the first pipe 41 of the heat exchanger 2 according to this embodiment.
  • the flow velocity of the heat medium decreases in the order of flows FL1, flows FL2, flows FL3, and flows FL4.
  • the flows FL1 are formed in a central part of the pipe, and have a high flow velocity.
  • the flows FL2 are formed in an outer part of the flows FL1, and have a flow velocity lower than that in the central part, but the flow velocity is relatively high.
  • the flows FL3 are formed in the vicinity of the inner peripheral surface S1 of the pipe, and have a low flow velocity.
  • the flows FL4 are formed in a part having the stagnation portion T formed therein, and have a lower flow velocity.
  • Fig. 2H indicates that the concave portions 41C are formed as illustrated in Fig. 2H , flows FL are formed over a range wider than in the case illustrated in Fig. 2G .
  • the flows FL2 are formed near the inner peripheral surface S1 of the first pipe 41, and the flows FL3 are formed in the stagnation portion T.
  • Fig. 2H indicates that the agitation of the heat medium is promoted by the action of the concave portions 41C, with the result that the flow velocity hardly falls even in the stagnation portion T.
  • the concave portions 41C are formed, the agitation of the heat medium is promoted, and hence it is possible to suppress a local temperature rise in the stagnation portion T, to thereby suppress precipitation of scale.
  • Fig. 3A is a graph showing a refrigerant temperature and a heat medium temperature of the heat exchanger 2 which are exhibited when the heat medium temperature at the outlet of the first flow path FP1 of the heat exchanger 2 is about 65 degrees Celsius.
  • Fig. 3B is a graph showing a refrigerant temperature and a heat medium temperature of the heat exchanger 2 which are exhibited when the heat medium temperature at the outlet of the first flow path FP1 of the heat exchanger 2 is about 90 degrees Celsius.
  • Fig. 3C is an explanatory diagram showing a relationship among the first region Rg1, the second region Rg2, and a boundary position "mp".
  • a tapping temperature is 65 degrees Celsius (the heat medium temperature of the heat medium flowing out of the outflow port 41b is 65 degrees Celsius)
  • a tapping temperature is 90 degrees Celsius (the heat medium temperature of the heat medium flowing out of the outflow port 41b is 65 degrees Celsius)
  • a temperature difference between the heat medium and the refrigerant on the outlet side (outlet side of the first flow path FP1) is large.
  • the refrigerant temperature is higher than the heat medium temperature by about 10 degrees Celsius to about 30 degrees Celsius in a range from the outflow port 41b as the outlet of the first flow path FP1 to a portion corresponding to a dimensionless distance of 0.1. Therefore, in the first pipe 41, a local temperature rise is liable to occur and scale tends to be precipitated in the range from the outflow port 41b as the outlet of the first flow path FP1 to the portion corresponding to the dimensionless distance of 0.1.
  • the dimensionless distance is a ratio of the length of a part of the first pipe 41 to the total length of the first pipe 41. When the dimensionless distance is 0.1, the dimensionless distance indicates the length of 1/10 of the first pipe 41.
  • this tendency applies to an increased tapping temperature, and the temperature difference between the heat medium and the refrigerant on the outlet side (outlet side of the first flow path FP1) is large.
  • the heat medium temperature itself is higher than that on the part on the inflow port 41a side.
  • the temperature difference between the heat medium and the refrigerant tends to be larger than that in the part on the inflow port 41a side. Therefore, in the part of the first pipe 41 on the outflow port 41b side, the heat medium temperature exhibited in the first pipe 41 locally increases, and the scale tends to be precipitated.
  • the heat exchanger 2 has the following configuration.
  • a position dividing a total length of the first pipe 41 into a length from the inflow port 41a and a length from the outflow port 41b in a ratio of six to four is set as the boundary position "mp".
  • the first region Rg1 is a part of the first pipe 41 ranging from the inflow port 41a to the boundary position "mp".
  • the second region Rg2 is a part of the first pipe 41 ranging from the boundary position "mp" to the outflow port 41b. In this manner, in the part of the first pipe 41 on the outflow port 41b side, the number of portions formed per unit length is increased.
  • the first pipe 41 is set to have the second region Rg2 ranging from the outflow port 41b as the outlet of the first flow path FP1 to a portion corresponding to a dimensionless distance of 0.4.
  • this setting it is possible to effectively suppress a local temperature rise in the range from the outflow port 41b as the outlet of the first flow path FP1 to the portion corresponding to the dimensionless distance of 0.1, to thereby suppress precipitation of scale.
  • the first region Rg1 and the second region Rg2 are defined not based on the second pipe 42 but based on the first pipe 41. More specifically, the first region Rg1 and the second region Rg2 are defined based on the inflow port 41a of the first pipe 41.
  • the present invention is not limited to this definition method.
  • the first region Rg1 and the second region Rg2 may be defined based on the outflow port 41b.
  • the first region Rg1 and the second region Rg2 may be defined based on a second pipe.
  • the protrusion amount of the crest portion 41A may be smaller than that in the part on the inflow port 41a side for the heat medium.
  • water becomes harder to stagnate in the stagnation portion T on the outflow port 41b side, and it is possible to suppress a local temperature rise in the first pipe 41, to thereby suppress precipitation of scale.
  • the protrusion amount of the crest portion 41A may be reduced from the same position as a position at which the number of formation of the concave portions 41C is to be increased.
  • the concave portions 41C can be formed by, for example, dimple processing. This means that the concave portions 41C are recessed in spot-like shapes.
  • the present invention is not limited to the concave portions 41C recessed in spot-like shapes, and the concave portions 41C may be recessed in a linear shape. In other words, the concave portions 41C may be formed in a groove shape.
  • the concave portion 41C is described as a concave portion having a circular shape, but the present invention is not limited thereto.
  • the concave portion 41C may be a quadrangle or another polygonal shape.
  • respective concave portions 41C are described as having the same shape, but the present invention is not limited thereto, and the respective concave portions 41C may have different shapes.
  • the shapes of the concave portions 41C may be different between the first region Rg1 and the second region Rg2.
  • Fig. 4A is an explanatory diagram of the first pipe 41 in which three threads are formed by crest portions 41A and three threads are formed by trough portions 41B.
  • Fig. 4B is an explanatory diagram of the first pipe 41 in which four threads are formed by crest portions 41A and four threads are formed by trough portions 41B.
  • Part (a) in Fig. 4A is a sectional view of the first pipe 41 taken along a direction in parallel with a direction in which the heat medium flows
  • part (b) in Fig. 4A is a sectional view taken along the line A-A of the part (a) of Fig. 4A .
  • Part (a) in Fig. 4B is a sectional view of the first pipe 41 taken along a direction in parallel with a direction in which the heat medium flows
  • part (b) in Fig. 4B(b) is a sectional view taken along the line B-B of the part (a) of Fig. 4B .
  • This embodiment has a mode in which one thread formed by crest portion 41A and one thread formed by trough portion 41B are formed in the first pipe 41, but the present invention is not limited thereto.
  • the modification example has a mode in which, as illustrated in Fig. 4A and Fig. 4B , a plurality of threads formed by crest portions 41A and a plurality of threads formed by trough portions 41B are formed in the first pipe 41.
  • crest portions 41A three threads are formed by crest portions 41A and three threads are formed by trough portions 41B. That is, a first crest portion 41A1, a second crest portion 41A2, and a third crest portion 41A3 are formed in the first pipe 41. In addition, a first trough portion 41B1, a second trough portion 41B2, and a third trough portion 41B3 are formed in the first pipe 41.
  • the first trough portion 41B1 is formed between the first crest portion 41A1 and the second crest portion 41A2.
  • the second trough portion 41B2 is formed between the second crest portion 41A2 and the third crest portion 41A3.
  • the third trough portion 41B3 is formed between the third crest portion 41A3 and the first crest portion 41A1.
  • crest portions 41A In Fig. 4B , four threads are formed by crest portions 41A and four threads are formed by trough portions 41B. That is, a first crest portion 41A1, a second crest portion 41A2, a third crest portion 41A3, and a fourth crest portion 41A4 are formed in the first pipe 41. In addition, a first trough portion 41B1, a second trough portion 41B2, a third trough portion 41B3, and a fourth crest portion 41A4 are formed in the first pipe 41.
  • the first trough portion 41B1 is formed between the first crest portion 41A1 and the second crest portion 41A2.
  • the second trough portion 41B2 is formed between the second crest portion 41A2 and the third crest portion 41A3.
  • the third trough portion 41B3 is formed between the third crest portion 41A3 and the fourth crest portion 41A4.
  • the fourth trough portion 41B4 is formed between the fourth crest portion 41A4 and the first crest portion 41A1.
  • the protrusion amount in the diameter-increasing direction DR1 for increasing the diameter of the first pipe 41 decreases. That is, as the number of threads formed by crest portions 41A increases, a shape that causes the heat medium to be harder to stagnate in the stagnation portion T is provided. Thus, it becomes easier to suppress a local temperature rise in the first pipe 41, and it also becomes easier to suppress precipitation of scale.
  • first pipe 41 may be configured such that the number of threads formed by crest portions 41A in the first region Rg1 and the number of threads formed by crest portions 41A in the second region Rg2 are different from each other.
  • the first pipe 41 may be configured such that the number of threads formed by crest portions 41A in the second region Rg2 is larger than the number of threads formed by crest portions 41A in the first region Rg1.
  • three threads formed by crest portions 41A and three threads formed by trough portions 41B be formed in the first region Rg1, and four threads formed by crest portions 41A and four threads formed by trough portions 41B be formed in the second region Rg2.
  • Fig. 4C is an explanatory diagram of a flow velocity distribution of the heat medium in the first pipe 41 in Fig. 4A .
  • Fig. 4D is an explanatory diagram of a flow velocity distribution of the heat medium in the first pipe 41 in Fig. 4B .
  • Fig. 5 is a block diagram of the controller Cnt.
  • the controller Cnt includes a determination unit 90A configured to determine whether or not scale has adhered and a calculation unit 90B configured to calculate the flow rate of the heat medium conveyed from the pump 5.
  • the controller Cnt also includes an actuator control unit 90C configured to control, for example, the expansion device 3, the compressor 1, and a fan 4A provided to the evaporator based on a determination result obtained by the determination unit 90A.
  • the controller Cnt further includes a target discharge refrigerant temperature setting unit 90D configured to set a target discharge refrigerant temperature of the compressor 1 and a maximum value setting unit 90E configured to set the maximum value of the target discharge refrigerant temperature set by the target discharge refrigerant temperature setting unit 90D.
  • the controller Cnt can determine whether precipitation (adhesion) of scale occurs in the first flow path FP1 by the following method.
  • the determination unit 90A of the controller Cnt determines that scale has adhered to the first flow path FP1.
  • the calculation unit 90B of the controller Cnt can acquire the calculated flow rate based on, for example, the heat medium temperature at the inlet of the first flow path FP1 and a target heat medium temperature (target outlet temperature) at the outlet of the first flow path FP1.
  • the controller Cnt can acquire the heat medium temperature at the inlet of the first flow path FP1 from a temperature detected by the detection unit 10C.
  • the actuator control unit 90C of the controller Cnt executes first control for increasing an opening degree of the expansion device 3.
  • the actuator control unit 90C of the controller Cnt may execute second control for reducing a rotation speed of the compressor 1 and third control for increasing a rotation speed of the fan 4A provided to the evaporator. That is, the controller Cnt executes at least one of the first control, the second control, or the third control. This can prevent the temperature of the heat medium flowing through the first pipe 41 from rising excessively, and prevents more scale from being precipitated in the first pipe 41.
  • the actuator control unit 90C of the controller Cnt controls the opening degree of the expansion device 3 so that the target discharge refrigerant temperature of the compressor 1 is approached.
  • the target discharge refrigerant temperature setting unit 90D of the controller Cnt can calculate the target discharge refrigerant temperature based on the outside air temperature and a predetermined target outlet temperature of the first flow path FP1.
  • the controller Cnt can acquire the outside air temperature from a temperature detected by the detection unit 10A.
  • the target discharge refrigerant temperature setting unit 90D of the controller Cnt is configured to reduce the target discharge refrigerant temperature when it is determined that scale has adhered to the first flow path FP1.
  • the actuator control unit 90C of the controller Cnt performs control so as to increase the opening degree of the expansion device 3. Therefore, it is possible to prevent the temperature of the heat medium flowing through the first pipe 41 from rising excessively, to thereby prevent a large amount of scale from being precipitated in the first pipe 41.
  • the maximum value setting unit 90E of the controller Cnt sets the maximum value of the target discharge refrigerant temperature of the compressor 1 to 70 degrees Celsius. This configuration is described next.
  • Fig. 6 is an explanatory graph of the solubility in the heat medium.
  • a curved line shown in Fig. 6 indicates the solubility in the heat medium in accordance with the temperature. As shown in Fig. 6 , the solubility of the scale in the heat medium decreases. Characteristics of the solubility exhibited when the heat medium temperature is equal to or lower than 40 degrees Celsius are indicated by a straight line L1. Meanwhile, characteristics of the solubility exhibited when the heat medium temperature is equal to or higher than 40 degrees Celsius are indicated by a straight line L2. As can be understood from the inclinations of the straight line L1 and the straight line L2, the solubility greatly changes with a heat medium temperature of about 40 degrees Celsius being assumed as a boundary.
  • the actuator control unit 90C of the controller Cnt controls a frequency of the compressor 1 based on, for example, the outside air temperature and the heat medium temperature at the inlet of the first flow path FP1.
  • the controller Cnt can acquire the outside air temperature from the temperature detected by the detection unit 10A.
  • the controller Cnt can further acquire the heat medium temperature at the inlet of the first flow path FP1 from the temperature detected by the detection unit 10C.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Details Of Fluid Heaters (AREA)
EP16911650.6A 2016-08-05 2016-08-05 Wärmetauscher und kältekreislaufvorrichtung mit dem wärmetauscher Active EP3495760B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2016/073070 WO2018025391A1 (ja) 2016-08-05 2016-08-05 熱交換器及びその熱交換器を備えた冷凍サイクル装置

Publications (3)

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EP3495760A1 true EP3495760A1 (de) 2019-06-12
EP3495760A4 EP3495760A4 (de) 2019-09-04
EP3495760B1 EP3495760B1 (de) 2022-08-10

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JP7199842B2 (ja) * 2018-06-15 2023-01-06 三菱重工サーマルシステムズ株式会社 水熱交換器、ガスクーラ

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JP2006266592A (ja) * 2005-03-24 2006-10-05 Hitachi Home & Life Solutions Inc ヒートポンプ給湯装置
JP2007218486A (ja) * 2006-02-15 2007-08-30 Hitachi Cable Ltd 熱交換器用伝熱管及びこれを用いた熱交換器
JP4867749B2 (ja) * 2007-03-28 2012-02-01 パナソニック株式会社 ヒートポンプ給湯装置
JP2008249163A (ja) * 2007-03-29 2008-10-16 Daikin Ind Ltd 給湯用熱交換器
JP2009041880A (ja) * 2007-08-10 2009-02-26 Sumitomo Light Metal Ind Ltd 給湯機用水熱交換器
JP2009097810A (ja) * 2007-10-18 2009-05-07 Mitsubishi Electric Corp 熱交換器
JP5151626B2 (ja) * 2008-04-02 2013-02-27 パナソニック株式会社 ヒートポンプ給湯装置
JP2009270755A (ja) * 2008-05-07 2009-11-19 Sumitomo Light Metal Ind Ltd 熱交換器用伝熱管及びそれを用いた熱交換器
JP5444127B2 (ja) * 2010-06-03 2014-03-19 日立アプライアンス株式会社 ヒートポンプ給湯機
JP5642462B2 (ja) * 2010-09-08 2014-12-17 株式会社Ｕａｃｊ銅管 熱交換器用伝熱管、及びこれを用いた熱交換器
JP5404589B2 (ja) * 2010-12-09 2014-02-05 三菱電機株式会社 捩り管形熱交換器
JP5573740B2 (ja) * 2011-03-18 2014-08-20 三菱電機株式会社 ヒートポンプ式給湯機
JP5776649B2 (ja) * 2012-08-24 2015-09-09 三菱電機株式会社 ヒートポンプ給湯機

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WO2018025391A1 (ja) 2018-02-08
EP3495760A4 (de) 2019-09-04
JPWO2018025391A1 (ja) 2019-03-07
JP6639678B2 (ja) 2020-02-05

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