EP3412991A1 - Système d'échange de chaleur et procédé de suppression de tartre pour système d'échange de chaleur - Google Patents

Système d'échange de chaleur et procédé de suppression de tartre pour système d'échange de chaleur Download PDF

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Publication number
EP3412991A1
EP3412991A1 EP16894555.8A EP16894555A EP3412991A1 EP 3412991 A1 EP3412991 A1 EP 3412991A1 EP 16894555 A EP16894555 A EP 16894555A EP 3412991 A1 EP3412991 A1 EP 3412991A1
Authority
EP
European Patent Office
Prior art keywords
shear stress
liquid
heat exchanger
stress pulse
opening
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
EP16894555.8A
Other languages
German (de)
English (en)
Other versions
EP3412991B1 (fr
EP3412991A4 (fr
Inventor
Kazuhiro Shigyo
Takafumi Nakai
Kazuhiro Miya
Shuhei NAITO
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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Filing date
Publication date
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Publication of EP3412991A1 publication Critical patent/EP3412991A1/fr
Publication of EP3412991A4 publication Critical patent/EP3412991A4/fr
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Publication of EP3412991B1 publication Critical patent/EP3412991B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D19/00—Details
    • F24D19/0092—Devices for preventing or removing corrosion, slime or scale
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B08—CLEANING
    • B08B—CLEANING IN GENERAL; PREVENTION OF FOULING IN GENERAL
    • B08B9/00—Cleaning hollow articles by methods or apparatus specially adapted thereto 
    • B08B9/02—Cleaning pipes or tubes or systems of pipes or tubes
    • B08B9/027—Cleaning the internal surfaces; Removal of blockages
    • B08B9/032—Cleaning the internal surfaces; Removal of blockages by the mechanical action of a moving fluid, e.g. by flushing
    • B08B9/0321—Cleaning the internal surfaces; Removal of blockages by the mechanical action of a moving fluid, e.g. by flushing using pressurised, pulsating or purging fluid
    • B08B9/0325—Control mechanisms therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D17/00—Domestic hot-water supply systems
    • F24D17/02—Domestic hot-water supply systems using heat pumps
    • 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
    • F24H9/00—Details
    • F24H9/0005—Details for water heaters
    • F24H9/0042—Cleaning arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28G—CLEANING OF INTERNAL OR EXTERNAL SURFACES OF HEAT-EXCHANGE OR HEAT-TRANSFER CONDUITS, e.g. WATER TUBES OR BOILERS
    • F28G13/00—Appliances or processes not covered by groups F28G1/00 - F28G11/00; Combinations of appliances or processes covered by groups F28G1/00 - F28G11/00

Definitions

  • the present invention relates to a heat exchange system which heats a to-be-heated liquid, for example, water to be applied to a shower or the like, and a scale reduction method for the heat exchange system.
  • Water heaters which supply hot water to a bathroom or a kitchen are roughly divided into, for example, electric water heaters, gas-fired water heaters such as gas boilers, and oil-fired water heaters. Such a water heater is provided with a heat exchanger for transferring heat to water.
  • electric water heaters in particular, heat pump water heaters, which are a heat-pump heat exchanger type of electric water heaters, have received attention from the viewpoint of saving energy and reduction of carbon dioxide, which is a countermeasure against global warming.
  • Such a heat pump water heater transfers heat of the atmosphere to a heat medium, and uses this heat to boil water. More specifically, the principle of a heat pump water heater is based on the following cooling energy cycle: heat generated when a heat medium is compressed to be in a gaseous form is transferred to water by a heat exchanger, and cold air generated when the heat medium is expanded is used to return the temperature of the heat medium to the atmospheric temperature.
  • a heat pump water heater based on the above cooling energy cycle utilizes the heat of the atmosphere, and can thus use more energy than the energy required to operate the water heater.
  • a heat exchanger performs heat exchange between a heat medium flowing in the heat exchanger and a fluid such as water, which flows over the surface of the heat exchanger. It is therefore important to keep the surface of the heat exchanger, which serves as a heat transfer surface, clean at all times. This is because when the surface of the heat exchanger gets dirty, the effective heat transfer surface area decreases, resulting in reduction of a heat transfer capacity. Furthermore, if such dirt accumulates, it may clog a flow passage of water or the like.
  • patent literatures 1 and 2 describe that generation of scale is restricted using a pulsating flow the amount of which is changed, and which is generated by applying pulsation to the pressure of water for hot water supply.
  • Heat pump water heaters described in patent literatures 1 and 2 each include a hot water tank, a heating circulation passage for drawing out hot water from a lower part of the hot water tank and returning the hot water to an upper part of the hot water tank, a heating heat exchanger which heats hot water in the heating circulation passage, a pulsation generating unit disposed upstream of the heating exchanger in the heating circulation passage to cause the hot water in the heating circulation passage to flow in a pulsational manner, a circulation unit which circulates the hot water in the heating circulation passage, and a controller which controls the pulsation generating unit and the circulation unit.
  • the controller causes the pulsation generating unit to operate to produce a pulsating flow, while heating is performed by the heating heat exchanger, and controls the circulation unit to make the flow quantity in the heating circulation passage greater than or equal to a predetermined value.
  • Such a heat pump water heater can reduce accumulation of scale in the heating heat exchanger even when water having a high hardness is boiled, and can also reduce the rate of clogging of pipes which is caused by scale, to thereby increase the life of the heat pump water heater.
  • Patent literature 3 describes that when water is pulsating, a greater shear stress acts when water flows at a constant rate, and it is possible to efficiently restrict adhesion of scale.
  • Patent Literature 1 Japanese Unexamined Patent Application Publication JP 2010-145 037
  • Patent Literature 2 Japanese Unexamined Patent Application Publication JP 2012-117 776
  • Patent Literature 3 Japanese Unexamined Patent Application Publication JP 2014-016 098 A
  • the present invention has been made in view of the above problem of the related art, and an object of the present invention is to provide a heat exchange system and a scale reduction method for the heat exchange system, which can more efficiently and reliably restrict generation and growth of scale on the heat exchanger.
  • a heat exchange system includes a first circulation circuit annularly provided to allow a first liquid to be circulated therein, a second circulation circuit annularly provided to allow a second liquid to be circulated therein, a heat exchanger which performs heat exchange between the first liquid and the second liquid, a pressure retention unit which pressurizes and retains a portion of the second liquid, an opening and closing mechanism unit disposed on an inlet side of the heat exchanger, into which the second liquid is to flow, the opening and closing mechanism unit being provided to switch the second liquid to be made to flow into the heat exchanger, from the second liquid from the second circulation circuit and the second liquid from the pressure retention unit, and a controller which controls the amount of pressure to be applied to the second liquid retained by the pressure retention unit, and controls the switching operation of the opening and closing mechanism unit.
  • the heat exchanger is supplied at a preset timing with a secondary-side target liquid to which a preset pressure has been applied. Thereby, it is possible to more efficiently and reliably reduce generation and growth of scale on the heat exchanger.
  • the heat exchange system heats or cools a secondary-side liquid such as water, with the heat of a primary-side liquid heated or cooled by a heat pump.
  • the heat exchange system restricts adhesion of scale which occurs on a contact surface of the heat exchanger, which contacts the secondary-side liquid, when it heats or cools of the secondary-side liquid.
  • FIG. 1 is a block diagram illustrating an example of the configuration of a heat exchange system 1 according to Embodiment 1 of the present invention.
  • the heat exchange system 1 includes a primary-side circulation circuit 10 serving as a first circulation circuit, a secondary-side circulation circuit 20 serving as a second circulation circuit, and a heat exchanger 2 disposed between the primary-side circulation circuit 10 and the secondary-side circulation circuit 20.
  • a primary-side to-be-heated liquid serving as a first liquid, which circulates in the primary-side circulation circuit 10
  • a secondary-side to-be-heated liquid serving as a second liquid, which circulates in the secondary-side circulation circuit 20.
  • the heat exchange system 1 heats the secondary-side to-be-heated liquid with the heat of the primary-side to-be-heated liquid.
  • the temperature of the primary-side to-be-heated liquid flowing in the primary-side circulation circuit 10 is controlled to be 60 degrees C
  • the temperature of the primary-side to-be-heated liquid on an outlet side of a heat pump 11 is controlled to be 65 degrees C.
  • the secondary-side to-be-heated liquid in the secondary-side circulation circuit 20 suppose the temperature of the secondary-side to-be-heated liquid on an outlet side of the heat exchanger 2 is 57 degrees C.
  • a sterilization operation which raises the temperature of the secondary-side to-be-heated liquid on the outlet side of the heat exchanger 2 to 65 degrees C is performed for just one hour, for example, once every two weeks for the purpose of removing bacteria from the secondary-side to-be-heated liquid.
  • the primary-side circulation circuit 10 includes the heat pump 11, a heater 12, a flow switching device 13, a first pump 14, a radiator 15, an expansion vessel 16, and the heat exchanger 2.
  • the heat pump 11, the heater 12, the expansion vessel 16, the flow switching device 13, the heat exchanger 2, and the first pump 14 are connected annularly by a pipe 17.
  • the radiator 15 is connected by a pipe 18, which is disposed between the flow switching device 13 and the first pump 14, and is different from the pipe 17.
  • the pipe 17 and the pipe 18 are connected such that the two pipes are branched off from the flow switching device 13, and join together at a point between the heat exchanger 2 and the first pump 14.
  • the heat pump 11 heats the primary-side to-be-heated liquid supplied by the first pump 14.
  • the heater 12 is provided to further heat the primary-side to-be-heated liquid supplied from the heat pump 11.
  • the heater 12 heats the primary-side to-be-heated liquid supplied from the heat pump 11, and supplies the heated primary-side to-be-heated liquid to the flow switching device 13.
  • the flow switching device 13 is, for example, an electromagnetic three-way valve including one inlet and two outlets. One of the outlets of the flow switching device 13 is selected to supply the primary-side to-be-heated liquid supplied from the heat pump 11 via the heater 12 to either the heat exchanger 2 or the radiator 15, thereby effecting switching between flow passages.
  • the first pump 14 is driven by a motor (not illustrated), and causes the primary-side to-be-heated liquid to be supplied from either the heat exchanger 2 or the radiator 15 to the heat pump 11.
  • the radiator 15 is, for example, a heat exchanger.
  • the radiator 15 performs heat exchange between the primary-side to-be-heated liquid flowing in the pipe 18 and indoor air in indoor space which is space to be air-conditioned, and heats the indoor air with the heat of the primary-side to-be-heated liquid.
  • the heat exchanger 2 performs heat exchange between the primary-side to-be-heated liquid flowing in the primary-side circulation circuit 10 and the secondary-side to-be-heated liquid flowing in the secondary-side circulation circuit 20, and heats the secondary-side to-be-heated liquid with the heat of the primary-side to-be-heated liquid.
  • the expansion vessel 16 is provided to temporarily store the primary-side to-be-heated liquid flowing out from the heater 12.
  • the secondary-side circulation circuit 20 includes a tank 21, a second pump 22, a scale trap 23, a pressure application unit 30 and the heat exchanger 2.
  • the tank 21, the second pump 22, the heat exchanger 2 and the scale trap 23 are annularly connected by a pipe 24 and a pipe 25.
  • the pressure application unit 30 is disposed in a flow passage which serves as a bypass circuit made up of a pipe 36 and a pipe 37, and which is different from a flow passage made up of the pipes 24 and 25 and located between the tank 21, the second pump 22 and the heat exchanger 2.
  • the tank 21 is supplied with the secondary-side to-be-heated liquid heated in the heat exchanger 2, and stores the secondary-side to-be-heated liquid.
  • the tank 21 is also supplied with tap water or the like from the outside via a feed pipe 21a, and the supplied tap water or the like is made to flow out from the tank 21 as the secondary-side to-be-heated liquid, and is then supplied to the second pump 22.
  • the heated secondary-side to-be-heated liquid stored in the tank 21 is discharged to the outside via a hot water pipe 21b, and used as hot water for a shower or the like.
  • the second pump 22 is driven by a motor (not illustrated), and causes water, which is the secondary-side to-be-heated liquid, to be suppled from the tank 21 to the heat exchanger 2.
  • the second pump 22 can change the quantity of the secondary-side to-be-heated liquid to be supplied to the heat exchanger 2, in accordance with the rotation speed of the motor.
  • the second pump 22 can increase the quantity of the secondary-side to-be-heated liquid to be supplied to the heat exchanger 2, by increasing the rotation speed of the motor.
  • the scale trap 23 is provided to trap scale which adhered to and was then removed from a contact surface of the heat exchanger 2 that contacts the secondary-side to-be-heated liquid.
  • the pressure application unit 30 is supplied with the secondary-side to-be-heated liquid from the tank 21.
  • the pressure application unit 30 applies a preset pressure to the secondary-side to-be-heated liquid supplied thereto, and then supplies the secondary-side to-be-heated liquid to the heat exchanger 2.
  • the pressure application unit 30 includes a third pump 31, a pressure retention unit 32, an opening and closing mechanism unit 33 and an opening and closing control unit 34.
  • the third pump 31 is driven by a motor (not illustrated), and causes a to-be-heated liquid to be supplied from the tank 21 to the pressure retention unit 32.
  • the pressure retention unit 32 is supplied with the secondary-side to-be-heated liquid from the tank 21 via the third pump 31.
  • the inside of the pressure retention unit 32 is filled with the secondary-side to-be-heated liquid at all times, and is subjected to application of a pressure higher than the pressure of the secondary-side to-be-heated liquid flowing in the pipe in the secondary-side circulation circuit 20.
  • FIG. 2 is a schematic diagram illustrating an example of the configuration of the pressure retention unit 32 as illustrated in FIG. 1 .
  • the pressure retention unit 32 includes a cylinder structure unit 32a which is formed in the shape of a hollow cylinder.
  • the cylinder structure unit 32a is provided with a solenoid valve 32b, a solenoid valve 32c, a water-quantity sensor 32d, a pressure sensor 32e, and a pressurizing unit 32f.
  • the solenoid valve 32b to the pressurizing unit 32f are connected to the opening and closing control unit 34 via a signal line 35.
  • the pressure retention unit 32 applies a preset pressure to the secondary-side to-be-heated liquid in the cylinder structure unit 32a.
  • the pressure retention unit 32 then causes the secondary-side to-be-heated liquid to flow out toward the opening and closing mechanism unit 33 to be described later via the pipe 37.
  • the solenoid valve 32b is disposed at the inlet of the pressure retention unit 32, through which the secondary-side to-be-heated liquid flowing through the pipe 36 via the third pump 31 flows.
  • the solenoid valve 32b supplies information indicating its open/closed state to the opening and closing control unit 34 via the signal line 35.
  • the open/closed state of the solenoid valve 32b is controlled based on a control signal supplied from the opening and closing control unit 34 via the signal line 35.
  • the solenoid valve 32c is provided at, for example, an upper part of the pressure retention unit 32.
  • the solenoid valve 32c supplies information indicating its open/closed state to the opening and closing control unit 34 via the signal line 35.
  • the open/closed state of the solenoid valve 32c is controlled based on a control signal supplied from the opening and closing control unit 34 via the signal line 35.
  • the solenoid valve 32b and the solenoid valve 32c are in "open” state.
  • the open/closed state of each of these valves is controlled by the opening and closing control unit 34 based on the result of detection which is supplied from the water-quantity sensor 32d to be described later.
  • the solenoid valve 32b and the solenoid valve 32c are controlled to be in "closed” state based on control by the opening and closing control unit 34.
  • the water-quantity sensor 32d detects the quantity of secondary-side to-be-heated liquid stored in the cylinder structure unit 32a, and supplies the result of this detection to the opening and closing control unit 34 via the signal line 35.
  • the pressure sensor 32e detects the pressure of the secondary-side to-be-heated liquid stored in the cylinder structure unit 32a, and supplies the result of this detection to the opening and closing control unit 34 via the signal line 35.
  • the pressurizing unit 32f is formed in the shape of a rod. When pushed into the cylinder structure unit 32a based on a control signal supplied from the opening and closing control unit 34 via the signal line 35, the pressurizing unit 32f applies a preset pressure to the secondary-side to-be-heated liquid stored in the cylinder structure unit 32a.
  • the cylinder structure unit 32a holds a state in which the pressure is applied to the secondary-side to-be-heated liquid, based on control by the opening and closing control unit 34. As a result, the secondary-side to-be-heated liquid in the cylinder structure unit 32a is kept subjected to the currently applied pressure.
  • the opening and closing mechanism unit 33 is, for example, a three-way valve.
  • the opening and closing mechanism unit 33 selects one of the secondary-side to-be-heated liquid which flows in the pipe 37 connected to the pressure retention unit 32 and the secondary-side to-be-heated liquid which flows in the pipe 24 connected to the second pump 22, and causes the selected secondary-side to-be-heated liquid to flow toward the heat exchanger 2.
  • the opening and closing mechanism unit 33 is adapted to keep the pressure application unit 30 and part of the secondary-side circulation circuit 20 which is located beside the tank 21, isolated from each other in pressure.
  • FIG. 3 is a schematic diagram illustrating an example of the configuration of the opening and closing mechanism unit 33 as illustrated in FIG. 1 .
  • the opening and closing mechanism unit 33 includes a solenoid valve 33a and a solenoid valve 33b.
  • the solenoid valve 33a is provided at the pipe 37 connected to the pressure retention unit 32.
  • the solenoid valve 33a supplies information indicating its open/closed state to the opening and closing control unit 34 via a signal line 38.
  • the open/closed state of the solenoid valve 33a is controlled based on a control signal supplied from the opening and closing control unit 34 via the signal line 38.
  • the solenoid valve 33a is provided with a metal shutter 33c.
  • the metal shutter 33c is operated based on control by the opening and closing control unit 34, and determines whether the solenoid valve 33a is to be in the open or closed state.
  • the metal shutter 33c includes, for example, a through hole located close to its center part. When the through-hole is aligned with the pipe 37, the solenoid valve 33a enters the "open" state.
  • the solenoid valve 33b is provided at the pipe 24 connected to the second pump 22.
  • the solenoid valve 33b supplies information indicating its open/closed state to the opening and closing control unit 34 via the signal line 38.
  • the open/closed state of the solenoid valve 33b is controlled based on a control signal supplied from the opening and closing control unit 34 via the signal line 38.
  • the solenoid valve 33b is provided with a metal shutter 33d.
  • the metal shutter 33d is operated based on control by the opening and closing control unit 34, and determines whether the solenoid valve 33b is to be in the open or closed state.
  • the metal shutter 33d includes, for example, a through hole located close to its center part. When the through hole is aligned with the pipe 24, the solenoid valve 33b enters the "open" state.
  • the opening and closing mechanism unit 33 is operated based on control by the opening and closing control unit 34 such that the solenoid valve 33a and the solenoid valve 33b operate in interlock with each other.
  • the metal shutter 33d is moved to cause the solenoid valve 33b to enter the "closed” state at the same time as the metal shutter 33c is moved to cause the solenoid valve 33a to enter the "open" state.
  • the opening and closing control unit 34 controls elements of the pressure retention unit 32 and those of the opening and closing mechanism unit 33.
  • the opening and closing control unit 34 receives the result of detection which is obtained by the water-quantity sensor 32d of the pressure retention unit 32 as illustrated in FIG. 2 . Based on information indicated by this result, the opening and closing control unit 34 supplies a control signal for controlling the opening and closing of the solenoid valve 32b and the solenoid valve 32c to the pressure retention unit 32 via the signal line 35.
  • the opening and closing control unit 34 receives from the pressure retention unit 32, the result of detection which is obtained by the pressure sensor 32e as illustrated in FIG. 2 . Based on information indicated by this result, the opening and closing control unit 34 supplies a control signal for controlling the operation of the pressurizing unit 32f to the pressure retention unit 32 via the signal line 35.
  • the opening and closing control unit 34 supplies at a preset timing, a control signal for controlling the opening and closing of the solenoid valve 33a and solenoid valve 33b of the opening and closing mechanism unit 33 as illustrated in FIG. 3 , to the opening and closing mechanism unit 33 via the signal line 38.
  • the primary-side to-be-heated liquid is supplied to the heat pump 11 by the first pump 14, and is then heated.
  • the heated primary-side to-be-heated liquid is re-heated by the heater 12, and then flows into the flow switching device 13.
  • the primary-side to-be-heated liquid flows out from the flow switching device 13 through the outlet for the flow toward the radiator 15. After flowing out from the flow switching device 13, the primary-side to-be-heated liquid flows into the radiator 15, where the primary-side to-be-heated liquid exchanges heat with indoor air, thereby heating the indoor air. Then, after flowing out from the radiator 15, the primary-side to-be-heated liquid flows into the first pump 14.
  • the primary-side to-be-heated liquid flows out from the flow switching device 13 through the outlet for the flow toward the heat exchanger 2.
  • the primary-side to-be-heated liquid flows into the heat exchanger 2, where the primary-side to-be-heated liquid exchanges heat with the secondary-side to-be-heated liquid, thereby heating the secondary-side to-be-heated liquid.
  • the primary-side to-be-heated liquid flows into the first pump 14.
  • the secondary-side to-be-heated liquid such as water which is supplied to the tank 21 flows out from the tank 21, and is then made to flow into the heat exchanger 2 by the second pump 22 via the pressure application unit 30.
  • the secondary-side to-be-heated liquid is heated by heat exchange with the primary-side to-be-heated liquid, and then flows out from the heat exchanger 2.
  • the secondary-side to-be-heated liquid flows into the tank 21 via the scale trap 23, and is stored in the tank 21.
  • the secondary-side to-be-heated liquid stored in the tank 21 is mixed with, for example, water, and used as hot water for a shower or the like.
  • the secondary-side to-be-heated liquid stored in the tank 21 is supplied to the pressure application unit 30.
  • the secondary-side to-be-heated liquid supplied to the pressure application unit 30 is made to flow into the pressure retention unit 32 by the third pump 31 of the pressure application unit 30.
  • the secondary-side to-be-heated liquid flows into the pressure retention unit 32, a preset pressure is applied to the secondary-side to-be-heated liquid based on control by the opening and closing control unit 34, and the secondary-side to-be-heated liquid then flows out from the pressure retention unit 32. After flowing out therefrom, the secondary-side to-be-heated liquid flows into the opening and closing mechanism unit 33.
  • the secondary-side to-be-heated liquid flows into the opening and closing mechanism unit 33, when the solenoid valve 33a, which is opened/closed based on control by the opening and closing control unit 34, is made to be in the "open" state, the secondary-side to-be-heated liquid flows out of the opening and closing mechanism unit 33 and flows into the heat exchanger 2.
  • the solenoid valve 33a disposed beside the pressure retention unit 32 and the solenoid valve 33b disposed beside the second pump 22 operate in interlock with each other such that one of the solenoid valve 33a and the solenoid valve 33b is controlled to be in the "open” state. Therefore, when the solenoid valve 33a is in the "open” state, only the secondary-side to-be-heated liquid present in the pressure retention unit 32 flows into the heat exchanger 2.
  • the opening/closing operation of the solenoid valve 33a and the pressure to be applied to the secondary-side to-be-heated liquid in the pressure retention unit 32 are controlled to cause the secondary-side to-be-heated liquid flowing out from the pressure retention unit 32 to flow into the heat exchanger 2 at a preset timing and with a preset pressure.
  • FIG. 4 is a flowchart illustrating the operation of the pressure application unit 30 as illustrated in FIG. 1 .
  • the solenoid valve 32c is made to be in the "open” state, and the solenoid valve 32b is made to be in the "open” state (steps S1 and S2). Then, the secondary-side to-be-heated liquid stored in the tank 21 is supplied to the pressure retention unit 32 by the third pump 31 (step S3).
  • the solenoid valve 32c is made to be in the "closed” state, and the solenoid valve 32b is made to be in the "closed” state, based on control by the opening and closing control unit 34 (steps S4 and S5).
  • a preset pressure is applied by the pressurizing unit 32f to the secondary-side to-be-heated liquid in the pressure retention unit 32 (step S6).
  • the pressure applied to the secondary-side to-be-heated liquid in the pressure retention unit 32 is held (step S7).
  • a control signal is transmitted from the opening and closing control unit 34 to the solenoid valve 33b of the opening and closing mechanism unit 33 (step S8).
  • the metal shutter 33d is slid based on the control signal to cause the solenoid valve 33b to be in the "closed" state (step S9).
  • a control signal is transmitted from the opening and closing control unit 34 to the solenoid valve 33a of the opening and closing mechanism unit 33 (step S10).
  • the metal shutter 33c is slid based on the control signal to cause the solenoid valve 33a to be in the "open" state (step S11).
  • the secondary-side to-be-heated liquid in the pressure retention unit 32 flows out from the pressure retention unit 32 and flows into the heat exchanger 2 (step S12).
  • a control signal is transmitted from the opening and closing control unit 34 to the solenoid valve 33a of the opening and closing mechanism unit 33 (step S13).
  • the metal shutter 33c is slid based on the control signal to cause the solenoid valve 33a to be in the "closed" state (step S14).
  • a control signal is transmitted from the opening and closing control unit 34 to the solenoid valve 33b of the opening and closing mechanism unit 33 (step S15).
  • the metal shutter 33d is slid based on the control signal to cause the solenoid valve 33b to be in the "open" state (step S16).
  • FIG. 5 is a graph illustrating an example of variation of a shear stress, which occurs with the passage of time in the case where the rotation speed of a motor in a conventional pump is increased.
  • Embodiment 1 for example, tap water is used as the secondary-side to-be-heated liquid to be stored in the tank 21.
  • a secondary-side to-be-heated liquid contains scale components such as oxides or carbonate compounds of metal ions represented by calcium. Therefore, when the secondary-side to-be-heated liquid is caused to exchange heat with the primary-side to-be-heated liquid by the heat exchanger 2, the scale components contained in the secondary-side to-be-heated liquid precipitate and adhere onto a contact surface of the heat exchanger 2 that contacts the secondary-side to-be-heated liquid. When the precipitating scale adheres onto the heat exchanger 2, the scale clogs the flow passage, thus reducing the heat exchange efficiency.
  • scale components such as oxides or carbonate compounds of metal ions represented by calcium. Therefore, when the secondary-side to-be-heated liquid is caused to exchange heat with the primary-side to-be-heated liquid by the heat exchanger 2, the scale components contained in the secondary-side to-be-heated liquid precipitate and
  • a pulsating flow is generated in a to-be-heated liquid, or the speed at which the to-be-heated liquid passes through a heat exchanger is increased, thereby generating a shear stress between the to-be-heated liquid and a contact surface of the heat exchanger which contacts the to-be-heated liquid.
  • scale precipitating on the contact surface of the heat exchanger is peeled off by the shear stress, to thereby restrict the growth of the scale.
  • the speed of the to-be-heated liquid be increased in general, it is done by increasing the rotation speed of the motor driving the pump which feeds the to-be-heated liquid. However, it takes some time to cause the rotation speed of the motor which drives the pump to reach a target rotation speed. Thus, as illustrated in FIG. 5 , for example, two seconds are required to obtain a target shear stress by increasing the rotation speed of the motor.
  • the secondary-side to-be-heated liquid subjected to application of a preset pressure is made to flow into the heat exchanger 2 at a preset timing, thereby giving a shear stress which can remove scale precipitating on the contact surface of the heat exchanger 2 that contacts the secondary-side to-be-heated liquid.
  • FIG. 6 is a schematic diagram for explaining a relationship between a bubble adhering to the contact surface of the heat exchanger 2 as illustrated in FIG. 1 and scale precipitating on the contact surface.
  • FIG. 7 is a schematic diagram illustrating an example of scale precipitating on the contact surface of the heat exchanger 2 as illustrated in FIG. 1 .
  • a micro layer 41 is formed at an interface between the bubble 40 and the contact surface of the heat exchanger 2, and in the micro layer 41, ions concentrate such that the concentration thereof is approximately 1.5 times greater than those in areas other than the interface.
  • a larger number of scale nuclei which are starting points of scale growth, precipitate than in areas to which no bubble 40 adheres.
  • a scale nucleus precipitates so as to conform to the shape of the bubble 40.
  • the scale precipitating in the above manner can be removed by applying a shear stress. At this time, if the nuclei of the scale adhering to the contact surface of the heat exchanger 2 have not yet grown, the scale can be removed by a smaller shear stress than that required to remove grown scale.
  • scale nuclei are minute as compared with grown scale, there is no risk that such scale nuclei will re-adhere to the surface of the heat exchanger 2, pipes or the like, or deposit on parts of the pipes which stagnate liquid flow. Accordingly, scale adhering in the form of scale nuclei can be removed efficiently with a lower flow quantity and a smaller shear stress than those required to remove grown scale.
  • FIG. 8 is a graph illustrating an example of a relationship between a shear stress and the diameter of each of bubbles 40 at the time when each bubble 40 is separated from the heat exchanger 2 as illustrated in FIG. 1 .
  • the greater the shear stress applied to the secondary-side to-be-heated liquid the smaller the diameter of the bubble 40 separated from the contact surface of the heat exchanger 2 that contacts the secondary-side to-be-heated liquid.
  • a shear stress of 50 Pa is applied to the secondary-side to-be-heated liquid, a bubble 40 having a diameter of approximately 100 ⁇ m can be separated from the contact surface of the heat exchanger 2.
  • FIG. 9 is a graph illustrating an example of variation of a shear stress, which occurs with the passage of time, in the case where the shear stress is applied to the secondary-side to-be-heated liquid in the heat exchange system 1 as illustrated in FIG. 1 .
  • the variation of the shear stress which is indicated by a dotted line, corresponds to the variation of the shear stress which occurs with the passage of time as illustrated in FIG. 5 .
  • a shear stress is applied in the manner of pulses to the secondary-side to-be-heated liquid (the shear stress applied in the manner of pulses will be hereinafter referred to as "shear stress pulses").
  • the applied shear stress rises steeply as compared with the case illustrated in FIG. 5 , as a result of which a target shear stress can be applied in a shorter time period to the bubbles 40 and scale nuclei that adhere to the heat exchanger 2. It is therefore possible to efficiently remove the scale nuclei and restrict the growth of the scale, as compared with the case illustrated in FIG. 5 .
  • bubbles 40 adhering to the contact surface of the heat exchanger 2 that contacts the secondary-side to-be-heated liquid are moved in accordance with the applied shear stress.
  • a shear stress of 50 Pa is applied for 0.5 seconds
  • a bubble 40 having a diameter of approximately 100 ⁇ m can be moved.
  • FIG. 10 is a graph illustrating an example of a relationship between the number of times a shear stress pulse is applied and the average diameter of the bubbles 40.
  • FIG. 10 illustrates by way of example the case where a shear stress of 50 Pa is applied to the secondary-side to-be-heated liquid at intervals of 0.5 seconds.
  • the average diameter of the bubbles 40 adhering to the contact surface of the heat exchanger 2 that contacts the secondary-side to-be-heated liquid increases as the number of times a shear stress pulse is applied increases.
  • the average diameter of the bubbles 40 is 1000 ⁇ m or greater. This is because when the shear stress pulse is applied a number of times, a plurality of bubbles 40 aggregate into a single larger bubble 40.
  • the greater the diameter of the bubble 40 the smaller the shear stress required to remove the bubble.
  • a shear stress pulse of 3.3 Pa it is possible to remove a bubble 40 of approximately 1000 ⁇ m into which a number of bubbles are aggregated.
  • Embodiment 1 such a great shear stress pulse as to have a great shear stress reaching a target shear stress is applied a number of times, to thereby cause the bubbles 40 to move and aggregate into a larger bubble, and then shear stress pulses to act a smaller shear stress than the above shear stress are applied. Thereby, it is possible to efficiently remove the bubbles 40 and scale nuclei which adhere to the heat exchanger 2, and restrict the growth of the scale.
  • FIG. 11 is a graph for explaining the amount of scale adhering to the heat exchanger 2 in the case of changing the timing of application of the shear stress pulse.
  • a shear stress pulse cycle was applied under conditions described below, and the shear stress pulse cycle is a combination of a first shear stress pulse having a preset shear stress and a second shear stress pulse having a smaller shear stress than that of the first shear stress. Then, the adhesion amount of scale on the heat exchanger 2 in the case where the heat exchange system 1 was operated for 100 hours while changing the intervals of application of the shear stress pulse cycle was measured.
  • FIG. 11 illustrates by way of example the adhesion amounts of scale which were measured when the shear stress pulse cycle was applied at intervals of 3 minutes, at intervals of 5 minutes and at the intervals of 7 minutes, respectively, the amounts being each expressed as a percent on the assumption that the adhesion amount of scale which was measured in the case of applying no shear stress pulse is 100%. Also, for reference, FIG. 11 illustrates results obtained in a pulsation operation involving pulsation produced by increasing the rotation speed of the motor in the conventional pump.
  • the amount of scale adhering to the heat exchanger 2 was 50% of that in the case where no shear stress pulse was applied. In the case where the shear stress pulse cycle was applied at intervals of five minutes, the amount of scale adhering to the heat exchanger 2 was 61% of that in the case where no shear stress pulse was applied. In the case where the shear stress pulse cycle was applied at intervals of seven minutes, the amount of scale adhering to the heat exchanger 2 was 65% of that in the case where no shear stress pulse was applied. It should be noted that in the conventional pulsation operation, the amount of scale adhering to the heat exchanger 2 was 73% of that in the case where no shear stress pulse was applied.
  • FIG. 12 is a graph for explaining the amount of scale adhering to the heat exchanger in the case of changing the shear stress of the shear stress pulse.
  • the shear stress pulse cycle is applied under conditions indicated below. Then, the adhesion amount of scale on the heat exchanger 2 in the case where the heat exchange system was operated for 100 hours on the condition that the shear stress pulse cycle was applied at intervals of five minutes was measured.
  • FIG. 12 illustrates by way of example the adhesion amounts of scale which were measured when first shear stress pulses having shear stresses 0 Pa to 70 Pa were applied, the amounts being each expressed on the assumption that the amount of scale adhered which was measured in the case of applying no shear stress pulse is "100".
  • the shear stress of the first shear stress pulse was greater than or equal to 5 Pa
  • the amount of scale adhering to the heat exchanger 2 was reduced as compared with the case where no shear stress pulse was applied.
  • the shear stress of the first shear stress pulse was greater than or equal to 50 Pa
  • the adhesion amount of scale was unchanged, and the scale reduction effect tended not to be further improved.
  • the shear stress of the first shear stress pulse when the shear stress of the first shear stress pulse is greater than or equal to 5 Pa, the scale reduction effect can be obtained, and when the shear stress of the first shear stress pulse is greater than or equal to 50 Pa, the scale reduction effect is not further improved. That is, it is preferable that the shear stress of the shear stress pulse be set to fall within the range of 5 to 50 Pa.
  • the shear stress of the second shear stress pulse is 3.3 Pa
  • the ratio between the shear stress of the first shear stress pulse and that of the second shear stress pulse be set to fall within the range "5:3.3” to "50:3.3".
  • FIG. 13 is a graph for explaining the amount of scale adhering to the heat exchanger 2 in the case of changing the pulse width of the shear stress pulses.
  • a shear stress pulse cycle was applied under conditions indicated below. Then, the adhesion amount of scale on the heat exchanger 2 in the case where the heat exchange system 1 was operated for 100 hours on the condition that the shear stress pulse cycle was applied at intervals of five minutes was measured.
  • FIG. 13 illustrates by way of example the adhesion amounts of scale which were measured when first shear stresses having pulse widths of 0 to 5.0 seconds were applied, the amounts being each expressed on the assumption that the adhesion amount of scale which was measured in the case of applying no shear stress pulse is "100".
  • the amounts of scale adhering to the heat exchanger 2 which were measured when the first shear stresses having pulse widths of 0 to 5.0 seconds were applied were all reduced as compared with that in the case where no shear stress pulse was applied.
  • the measured amount of scale adhered were less than or equal to 70%, and the scale reduction effect tends to be further improved.
  • the scale can be reduced in a shorter time period, whereas it takes approximately 2 seconds to reduce the scale with such a control of the pump as described above.
  • the fourth investigation is a combination of the second investigation and the third investigation.
  • FIG. 14 is a table for explaining the amount of scale adhering to the heat exchanger 2 in the case of changing the shear stress and pulse width of the shear stress pulse.
  • a shear stress pulse cycle was applied under conditions described below. Then, the adhesion amount of scale on the heat exchanger 2 in the case where the heat exchange system 1 was operated for 100 hours on the condition that the shear stress pulse cycle was applied at intervals of five minutes was measured.
  • FIG. 14 illustrates by way of example results of scale reduction effects on the assumption that the adhesion amount of scale in the case of applying no shear stress pulse is "100".
  • "-" denotes results that the scale reduction effect was greater than or equal to 20%, that is, results that the adhesion amount of scale was less than or equal to 80%
  • "+” denotes results that the scale reduction effect was less than 20%, that is, results that the amount of scale deposition exceeded 80%.
  • Embodiment 1 there are provided; the primary-side circulation circuit 10 which is annularly provided, and in which the primary-side to-be-heated liquid is circulated; the secondary-side circulation circuit 20 which is annularly shaped, and in which the secondary-side to-be-heated liquid is circulated; the heat exchanger 2 which performs heat exchange between the primary-side to-be-heated liquid and the secondary-side to-be-heated liquid; the pressure retention unit 32 which pressurizes and retains a portion of the secondary-side to-be-heated liquid; the opening and closing mechanism unit 33 disposed on a side of the heat exchanger 2, into which the secondary-side to-be-heated liquid flows, the opening and closing mechanism unit 33 being provided to switch the secondary-side to-be-heated liquid to be made to flow into the heat exchanger 2 between the secondary-side to-be-heated liquid from the secondary-side circulation circuit 20 and the secondary-side to-be-heated liquid from the pressure retention unit 32; and the opening and
  • the opening and closing control unit 34 controls the pressure retention unit 32 and the opening and closing mechanism unit 33 such that a secondary-side to-be-heated liquid to which a shear stress pulse cycle is applied is supplied to the heat exchanger 2, the shear stress pulse cycle being a combination of a plurality of shear stress pulses having different shear stresses.
  • the shear stress pulse cycle is a combination of a first shear stress pulse and a second shear stress pulse having a smaller shear stress than that of the first shear stress pulse, which is achieved such that the first and second shear stress pulses are combined in this order.
  • the large bubble can be removed by applying the second shear stress pulse.
  • the heat exchange system according to Embodiment 2 is different from that of Embodiment 1 on the point that it includes a second pressure-application unit.
  • the secondary-side to-be-heated liquid is boiled up when it is circulated a number of times between the tank 21 and the heat exchanger 2 (this will be hereinafter referred to as "multiple-boiling system" as appropriate).
  • FIG. 15 is a block diagram illustrating an example of the heat exchange system 1 according to Embodiment 2.
  • elements identical to those of Embodiment 1 mentioned above will be denoted by the same reference signs, and their detailed descriptions will be omitted.
  • the heat exchange system 1 includes the primary-side circulation circuit 10, the secondary-side circulation circuit 20, and the heat exchanger 2.
  • the secondary-side circulation circuit 20 is provided with a second pressure-application unit 50, in addition to components similar to those of Embodiment 1.
  • the second pressure application unit 50 includes a fourth pump 51, a second pressure retention unit 52 connected to the fourth pump 51 by a pipe 56, and a second opening and closing mechanism unit 53 connected to the second pressure retention unit 52 by a pipe 57.
  • the fourth pump 51 has a similar configuration and a similar function to those of the third pump 31.
  • the second pressure retention unit 52 also has a similar configuration and a similar function to those of the pressure retention unit 32.
  • FIG. 16 is a schematic diagram illustrating an example of the configuration of the second opening and closing mechanism unit 53 as illustrated in FIG. 15 .
  • the second opening and closing mechanism unit 53 includes a solenoid valve 53a and a solenoid valve 53b.
  • the solenoid valve 53a is provided at the pipe 57 connected to the second pressure retention unit 52.
  • the solenoid valve 53a supplies information indicating its open/closed state to the opening and closing control unit 34 via a signal line 58. Furthermore, the open/closed state of the solenoid valve 53a is controlled based on a control signal supplied from the opening and closing control unit 34 via the signal line 58.
  • the solenoid valve 53a is provided with a metal shutter 53c.
  • the metal shutter 53c is operated based on control by the opening and closing control unit 34, and determines whether the solenoid valve 53a is to be in the open or the closed state.
  • the metal shutter 53c includes, for example, a through hole located close to its central part. When the through hole is aligned with the pipe 57, the solenoid valve 53a is made to be in the "open" state.
  • the solenoid valve 53b is provided at the pipe 25 connected to the tank 21.
  • the solenoid valve 53b supplies information indicating its open/closed state to the opening and closing control unit 34 via the signal line 58. Furthermore, the open/closed state of the solenoid valve 53b is controlled based on a control signal supplied from the opening and closing control unit 34 via the signal line 58.
  • the solenoid valve 53b is provided with a metal shutter 53d.
  • the metal shutter 53d is operated based on control by the opening and closing control unit 34, and determines whether the solenoid valve 53b is to be in the open or the closed state.
  • the metal shutter 53d includes, for example, a through hole located close to its central part. When the through hole is aligned with the pipe 25, the solenoid valve 53b is made to be in the "open" state.
  • the second opening and closing mechanism unit 53 is operated based on control by the opening and closing control unit 34 such that the solenoid valve 53a and the solenoid valve 53b operate in interlock with each other.
  • the metal shutter 53d is moved to cause the solenoid valve 53b to be in the "closed” state at the same time as the metal shutter 53c is moved to cause the solenoid valve 53a to be in the "open” state.
  • the solenoid valve 53a and the solenoid valve 53b are formed to have the above configurations in order that these valves can more quickly respond to control by the opening and closing control unit 34.
  • the opening and closing control unit 34 controls components of the second pressure retention unit 52 and components of the second opening and closing mechanism unit 53.
  • the opening and closing control unit 34 supplies a control signal for controlling an operation of the second pressure retention unit 52 to the second pressure retention unit 52 via a signal line 55. Furthermore, the opening and closing control unit 34 supplies, at a preset timing, a control signal for controlling the opening and closing of the solenoid valve 53a and solenoid valve 53b of the second opening and closing mechanism unit 53 provided as illustrated in FIG. 16 , to the second opening and closing mechanism unit 53 via the signal line 58.
  • the opening and closing control unit 34 is provided independently from the pressure application unit 30.
  • the opening and closing control unit 34 is not limited to that of the example.
  • the opening and closing control unit 34 may be included in the pressure application unit 30 as in Embodiment 1, or may be included in the second pressure-application unit 50.
  • the flow of the primary-side to-be-heated liquid in the primary-side circulation circuit 10 and the flow of the secondary-side to-be-heated liquid in the secondary-side circulation circuit 20 are similar to those in Embodiment 1.
  • the operation of the pressure application unit 30 is also similar to that in Embodiment 1.
  • the secondary-side to-be-heated liquid stored in the tank 21 is supplied to the second pressure-application unit 50.
  • the secondary-side to-be-heated liquid supplied to the second pressure-application unit 50 is made to flow into the second pressure retention unit 52 by the fourth pump 51 of the second pressure-application unit 50.
  • the secondary-side to-be-heated liquid in the second pressure retention unit 52 is subjected to application of a preset pressure based on control by the opening and closing control unit 34, and then flows out from the second pressure retention unit 52. After flowing out from the second pressure retention unit 52, the secondary-side to-be-heated liquid flows into the second opening and closing mechanism unit 53.
  • the secondary-side to-be-heated liquid in the second opening and closing mechanism unit 53 flows out from the second opening and closing mechanism unit 53 and flows into the heat exchanger 2, when the solenoid valve 53a, which is opened/closed based on control by the opening and closing control unit 34, is made to be in the "open" state.
  • the opening/closing operation of the solenoid valve 53a and the pressure to be applied to the secondary-side to-be-heated liquid in the second pressure retention unit 52 are controlled, to thereby cause the secondary-side to-be-heated liquid flowing out from the second pressure retention unit 52 to flow into the heat exchanger 2 at a preset timing and with a preset pressure.
  • the secondary-side to-be-heated liquid flowing from the second pressure retention unit 52 into the heat exchanger 2 is subjected to application of a shear stress pulse within the heat exchanger 2, which is performed in an opposite direction to the direction of application of a shear stress pulse to the secondary-side to-be-heated liquid flowing from the pressure retention unit 32 into the heat exchanger 2.
  • a shear stress pulse in the opposite direction is applied as a third shear stress pulse between the first shear stress pulse and the second shear stress pulse having a smaller shear stress than that of the first shear stress pulse, which are described above with respect to Embodiment 1.
  • the third shear stress pulse is equivalent to the first shear stress pulse except for the direction of application of the shear stress pulse.
  • the first shear stress pulse which acts to push bubbles in a direction toward the interior of the heat exchanger 2 is applied to cause the bubbles to be moved and aggregated
  • the third shear stress pulse which acts to pull the bubbles back in a direction away from the interior of the heat exchanger 2 is applied.
  • the bubbles 40 and scale nuclei adhering to the surface of the heat exchanger 2 that contacts the secondary-side to-be-heated liquid are more efficiently removed than in the case where only the first and second shear stress pulses are applied.
  • a shear stress pulse cycle which is provided by adding a third shear stress pulse to the first and second shear stress pulses according to Embodiment 1 is applied to the heat exchanger 2, the third shear stress pulse being applied to the heat exchanger 2 in the opposite direction to the direction in which the first and second shear stress pulses are applied.
  • FIG. 17 is a graph for explaining the amount of scale adhering to the heat exchanger 2 in the case where the first to third shear stress pulses are applied.
  • a shear stress pulse cycle was applied under conditions given below, and the applied shear stress pulse cycle is a combination of the first shear stress pulse having a preset shear stress, the second shear stress pulse having a smaller shear stress than that of the first shear stress pulse, and the third shear stress pulse which is equivalent to first shear stress pulse, and is applied to the heat exchanger 2 in the opposite direction to that of the first shear stress pulse.
  • the adhesion amount of scale on the heat exchanger 2 in the case where the heat exchange system 1 was operated for 100 hours while changing the intervals of application of the shear stress pulse cycle was measured. It should be noted that the first shear stress pulse, the third shear stress pulse and the second shear stress pulse are applied in this order.
  • FIG. 17 illustrates by way of example the adhesion amounts of scale which were measured when the shear stress pulse cycle is applied at intervals of 3 minutes, the amounts being each expressed as a percent on the assumption that the adhesion amount of scale which was measured when no shear stress pulse was applied is 100%.
  • the case of applying no shear stress pulse is referred to as "comparative example 1”
  • the case of applying a shear stress pulse cycle in which the first shear stress, the third shear stress and the second shear stress were applied in this order is referred to as “example 1”.
  • the case of applying a shear stress pulse cycle in which the first shear stress pulse and the second shear stress pulse were applied in this order as in Embodiment 1 is referred to as "comparative example 2".
  • the adhesion amount of scale on the heat exchanger 2 was 50% of that of comparative example 1 in which no shear stress pulse was applied. Furthermore, in example 1 in which the shear stress pulse cycle was applied such that the first shear stress pulse, the third shear stress pulse and the second shear stress pulse were applied in this order, the adhesion amount of scale on the heat exchanger 2 is 35% of that of comparative example 1.
  • the heat exchanger 2 is supplied with a secondary-side to-be-heated liquid subjected to application of a shear stress pulse cycle in which the first shear stress pulse, the third shear stress pulse and the second shear stress pulses are to be applied in this order. Thereby, it is possible to further efficiently and further reliably restrict generation and growth of scale.
  • the heat exchange system according to Embodiment 3 is different from Embodiment 2 in that the scale trap 23 provided in the secondary-side circulation circuit 20 is omitted.
  • the secondary-side to-be-heated liquid is circulated between the tank 21 and the heat exchanger 2 once, whereby it is boiled up (this will be hereinafter referred to as "single-boiling system").
  • the degree of a scale trapping effect obtained by the scale trap 23 as illustrated in FIG. 15 is smaller than that in the case where the secondary-side to-be-heated liquid is circulated a number times between the tank 21 and the heat exchanger 2, and the above single circulation can be hardly expected to reduce adhesion of scale on the heat exchanger 2.
  • the adhesion amount of scale on the heat exchanger 2 is larger than that in the same amount of secondary-side to-be-heated liquid as in the above case is circulated a number of times to be boiled up.
  • a shear stress pulse cycle similar to that in Embodiment 2 is applied also in the single-boiling system, to thereby reduce the adhesion amount of scale on the heat exchanger 2.
  • the number of times the secondary-side to-be-heated liquid needs to be circulated until it is boiled up depends on, for example, energy characteristics which varies in accordance with the kind of refrigerant for use in the heat pump. For example, if fluorocarbon gas such as R410 is used as a secondary-side to-be-heated liquid, when the secondary-side to-be-heated liquid is circulated a number of times, it is boiled up with a high energy efficiency.
  • FIG. 18 is a block diagram illustrating an example of the heat exchange system 1 according to Embodiment 3 of the present invention.
  • elements identical to those of embodiments 1 and 2 mentioned above will be denoted by the same reference signs, and their descriptions will be omitted.
  • the heat exchange system 1 includes the primary-side circulation circuit 10, the secondary-side circulation circuit 20 and the heat exchanger 2. However, unlike the heat exchange system 1 according to Embodiment 2 illustrated in FIG. 15 , the scale trap 23 is removed.
  • Embodiment 3 a shear stress pulse cycle including first to third shear stress pulses is applied to the heat exchanger 2 as in Embodiment 2.
  • FIG. 19 is a graph for explaining the adhesion amounts of scale on the heat exchanger 2 in the case where the first to third shear stress pulses are applied.
  • a shear stress pulse cycle is applied under conditions given below, and the shear stress pulse cycle is a combination of a first shear stress pulse having a preset shear stress, a second shear stress pulse having a smaller shear stress than that of the first shear stress pulse and a third shear stress pulse which has a shear stress equal to that of the first shear stress pulse, and which is applied to the heat exchanger 2 in the opposite direction to the direction of application of the first shear stress pulse.
  • the first shear stress pulse, the third shear stress pulse and the second shear stress pulse are applied in this order.
  • the adhesion amount of scale on the heat exchanger 2 As to the adhesion amount of scale on the heat exchanger 2, the adhesion amount of scale at the time when 2000 liters (L) of secondary-side to-be-heated liquid was boiled up was measured. This is because the adhesion amount of scale on the heat exchanger 2 at the time when for example, 200 liters of secondary-side to-be-heated liquid which corresponds to the capacity of a single tank 21 was boiled up was not sufficient for evaluation, and thus in order to properly evaluate the adhesion amount of scale, it was necessary to measure the adhesion amount of scale at the time when the above quantity of secondary-side to-be-heated liquid, which corresponds to the capacity of ten tanks 21, was boiled up.
  • the case in which the scale trap 23 was provided and the multiple-boiling system was adopted as in Embodiment 2, and no shear stress pulse was applied is referred to as the above "comparative example 1", and the adhesion amount of scale on the heat exchanger 2 in this case is defined as 100%.
  • the secondary-side to-be-heated liquid was circulated 100 times between the tank 21 and the heat exchanger 2.
  • Example 2 the case where the scale strap 23 was not provided, the single-boiling system was adopted, and a shear stress pulse cycle in which the first shear pulse, the third shear pulse and the second shear pulse were applied in this order was applied is referred to as "example 2".
  • the multiple-boiling system was adopted and a shear stress pulse cycle in which the first shear pulse, the third shear pulse and the second shear stress pulse were applied in this order was applied as in Embodiment 2 is referred to as "example 1".
  • Example 3 the case in which the single-boiling system was adopted as in Embodiment 3 but no shear stress pulse is applied.
  • the adhesion amount of scale can be greatly reduced as compared with the case where no shear stress pulse is applied; that is, it is reduced from 215% to 58%. Also, in the multiple-boiling system, the adhesion amount of scale is reduced from 100% to 35% by applying shear stress pulses; that is, a reduction effect of 65% can be obtained.
  • the adhesion amount of scale is reduced from 215%, which is the adhesion amount of scale in comparative example 3, to 58%, which is the adhesion amount of scale in example 2, and a reduction effect of 157% can be obtained. That is, a greater reduction effect can be attained for the one-time boiling system than in the multiple-boiling system.
  • the heat exchanger 2 is supplied with a secondary-side to-be-heated liquid subjected to application of a shear stress pulse cycle in which the first, third, and second shear stress pulses are applied in this order as in Embodiment 2.
  • a shear stress pulse cycle in which the first, third, and second shear stress pulses are applied in this order as in Embodiment 2.
  • embodiments 1 to 3 refers to by way of example the heat exchange system 1 in which the heat of the primary-side to-be-heated liquid heated by the heat pump 11 is used to heat the secondary-side to-be-heated liquid
  • the heat exchange system 1 is not limited to such an example.
  • a heat exchange system 1 in which the heat of the primary-side liquid cooled by the heat pump 11 is used to cool the secondary-side liquid may be applied.
  • the heat exchange system 1 may include no tank 21.
  • the heat exchange system 1 is provided with a passage into which a passage allowing the secondary-side to-be-heated liquid to be circulated in the secondary-side circulation circuit 20 branches.
  • the pressure application unit 30 is supplied with the secondary-side to-be-heated liquid flowing in the passage provided as the above branch. Thereby, it is possible to efficiently remove bubbles 40 and scale nuclei adhering to the contact surface of the heat exchanger 2, in the same manner as described above.
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JP5811053B2 (ja) 2012-07-09 2015-11-11 三菱電機株式会社 熱交換器およびその運転方法
JP5971149B2 (ja) * 2013-02-18 2016-08-17 三菱電機株式会社 給湯機
EP2980584B1 (fr) * 2013-03-29 2018-09-12 Mitsubishi Electric Corporation Procédé de vérification de la qualité de l'eau, dispositif de vérification de la qualité de l'eau et système d'alimentation d'eau chaude

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WO2017158938A1 (fr) 2017-09-21
EP3412991A4 (fr) 2019-03-20
JPWO2017158938A1 (ja) 2018-03-22
JP6239199B1 (ja) 2017-11-29

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