JP5743489B2 - Water treatment system - Google Patents

Description

  The present invention relates to a water treatment system, and more particularly to a water treatment system using a heat pump.

  A water treatment system such as a pure water production system is constituted by connecting various devices for water treatment with pipes. Examples of these devices include ion exchange devices, reverse osmosis membrane (RO membrane) devices, and filtration devices. Each device has an optimal water temperature range in order to maximize performance (impurity removal characteristics, etc.). On the other hand, for use points (use points), various temperatures such as 25 ° C., 60 ° C., and 80 ° C. may be required. Moreover, in the site | part which performs a circulating operation, the temperature of circulating water becomes easy to rise by the heat input from the pump accompanying a circulating operation, etc. As described above, in the water treatment system, it is necessary to adjust the temperature at various points in the system due to various factors such as the temperature requirement of the apparatus, the system requirement, and the system configuration.

  Patent Document 1 discloses an apparatus for producing ultrapure water. The raw water supplied from the raw water tank is processed in a degassing tank or RO membrane device and sent to a subsequent process. Since the standard design temperature of the reverse osmosis membrane in the RO membrane device is 25 ° C., in order to adjust the temperature of the treated water at the entrance point of the RO membrane device to this temperature, some heat is generated between the raw water tank and the deaeration tank. An exchange is installed.

  Patent Document 2 discloses an example in which a heat pump is used in a water treatment system for heat exchange. Heat pumps are known as energy efficient water treatment systems. The heat pump takes heat from an external heat source and supplies the taken heat to the heating target part, or takes heat from the cooling target part and releases the taken heat to the outside.

JP 2009-183800 A JP 2002-16036 A

  Conventionally, when adjusting the temperature of the water to be treated that circulates in the water treatment system, it has been common to provide equipment such as a cooling tower and a boiler. For example, when a boiler is used for heating, hot water or steam having a temperature higher than that of the heating target part is manufactured by the amount of heat input to the boiler, and the heat of the hot water or steam that is the heating medium is heated. Added to. When a cooling tower is used for cooling, cooling water having a temperature lower than that of the cooling target portion is produced, and heat is taken away from the cooling target portion.

  In the case of a water treatment system, many parts are controlled to a temperature close to room temperature. For example, the temperature of hot water or steam obtained in a boiler is much higher than the water temperature in the water treatment system. For this reason, when transporting warm water or steam by piping, there is a possibility that a large heat dissipation loss occurs.

  Unlike a boiler or the like, a heat pump is advantageous as a temperature adjusting means in a water treatment system because it is not necessary to heat a heat medium to an excessively high temperature. In addition, it is more energy efficient than a boiler or the like, and it is easy to reduce power consumption. However, the water temperature in the water treatment system fluctuates due to various causes, such as temperature changes during the day and night. On the other hand, various apparatuses in the water treatment system are configured to operate in an optimal water temperature range, and it is necessary to appropriately cope with fluctuations in temperature conditions with a heat pump. The temperature range required at the point of use is also strictly controlled depending on the intended use. If the heat pump has an excessive capacity (compressor capacity), it is possible to mitigate the effects of fluctuations in temperature conditions, but it has a significant effect on cost.

  This invention is made | formed in view of such a subject, and it aims at providing the water treatment system which can suppress the increase in heat pump capacity | capacitance easily, and a water treatment system using the same.

Water treatment system of the present invention includes a plurality of water treatment apparatus, by connecting a plurality of water treatment apparatus adjacent to each other, the plurality of pipes sections through the internal water, at least one pipe section as endothermic pipe section A heat pump that absorbs heat from the endothermic piping section and exhausts the heat absorbed from the endothermic piping section to the exhaust heat piping section with at least one other piping section as an exhaust heat piping section, and a heat pump and an endothermic piping section. Heat storage means for temporarily storing at least a part of the heat quantity that can be exchanged between them or at least a part of the heat quantity that can be exchanged between the heat pump and the exhaust heat pipe section.
In one embodiment, the water treatment system further includes a first heat storage means provided on the downstream side of the connection portion with the heat pump in the endothermic piping section, and a branching from the endothermic piping section on the upstream side of the connecting portion, A first bypass pipe that merges with the endothermic pipe section on the downstream side of the storage means.
In another embodiment, the water treatment system further branches from the endothermic piping section on the upstream side of the first heat storage means provided on the downstream side of the connection portion with the heat pump in the endothermic piping section, A first bypass pipe that joins the endothermic pipe section downstream of the first heat storage means; and from the first heat storage means upstream of the connecting portion and downstream of the branch portion of the first bypass pipe. And a first reflux pipe for refluxing water in the endothermic piping section.
In another embodiment, the water treatment system is further thermally connected to each of the endothermic piping section and the heat pump, and a first heat medium for transferring heat between the water flowing through the endothermic piping section and the heat pump is provided. The first intermediate loop made to flow and the first intermediate loop branch along the flow direction of the first heat medium downstream of the connection portion with the heat pump, and the connection portion with the endothermic piping section A first intermediate loop bypass pipe that joins upstream and a third intermediate loop bypass pipe that is provided in the first intermediate loop bypass pipe and temporarily stores at least a part of the first heat medium that flows through the first intermediate loop. Heat storage means.
In another embodiment, the water treatment system is further thermally connected to each of the endothermic piping section and the heat pump, and a first heat medium for transferring heat between the water flowing through the endothermic piping section and the heat pump is provided. A third intermediate loop adapted to flow, and third heat storage means for temporarily storing at least a portion of the first heat medium, wherein the third intermediate loop includes an endothermic piping section; A first circulation loop which is thermally connected and through which the first heat medium circulates via the third heat storage means; and is thermally connected to the heat pump and via the third heat storage means. And a second circulation loop in which the first heat medium is circulated.

  The amount of heat transferred to and from the heat pump by the water flowing through the endothermic piping section or the exhaust heat piping section may be insufficient or excessive with respect to the amount of heat necessary for heating or cooling the water. This occurs mainly due to temperature fluctuations in water, but can also be caused by changes in the flow rate of water, physical properties (heat capacity, etc.), or temporary changes in the target heating temperature (or target cooling temperature) of water. In this embodiment, heat that temporarily stores at least part of the heat quantity that can be exchanged between the heat pump and the endothermic piping section, or at least part of the amount of heat that can be exchanged between the heat pump and the exhaust heat pipe section. A storage means is provided, and an excess amount of heat can be stored. Therefore, when the heat storage means stores an excessive amount of heat, the temperature condition of the water changes, and the amount of heat necessary to change the water to the desired temperature exceeds the amount of heat that can be supplied by the heat pump. In such a case, it is possible to use an excess amount of heat stored in the heat storage means.

  Thus, according to the present invention, it is possible to provide a water treatment system that can easily suppress an increase in heat pump capacity and a water treatment system using the water treatment system.

It is a conceptual diagram which shows 1st Embodiment of the water treatment system of this invention. It is a schematic diagram which shows notionally the effect | action of the water treatment system shown in FIG. It is a schematic diagram which shows the energy utilization efficiency of the water treatment system shown in FIG. 1, and another water treatment system. It is a conceptual diagram which shows 2nd Embodiment of the water treatment system of this invention. It is a conceptual diagram which shows 3rd Embodiment of the water treatment system of this invention. It is a conceptual diagram which shows 4th Embodiment of the water treatment system of this invention. It is the schematic which shows an example of a structure of a water treatment system. It is the schematic which shows the other example of a structure of a water treatment system. It is the schematic which shows the line structure at the time of the hot water sterilization of a water treatment system. It is the schematic which shows the structure of the water treatment system of an Example. It is a graph which shows a time-dependent change of the excess and deficiency heat amount of an Example and each comparative example.

  With reference to FIGS. 1-6, some embodiment which concerns on the water treatment system of this invention which can be used conveniently with a water treatment system is described. These figures extract and show only the part relevant to each embodiment among various apparatuses which comprise a water treatment system. An example of an actual water treatment system will be described later. The present invention can be particularly suitably used in a water treatment system, but can be applied to any system that requires temperature adjustment of a fluid.

(First embodiment)
Referring to FIG. 1A, a water treatment system 1a includes a heat absorption pipe section 2 that connects a plurality of adjacent devices D1 and D2, and a heat pump 3 that is thermally connected to a part of the heat absorption pipe section 2. And a first heat storage means 4 and a first bypass pipe 5. The endothermic piping section 2 is an arbitrary piping section that requires cooling in the water treatment system. In the endothermic piping section 2, water normally flows, but any fluid including a liquid or gas other than water may flow.

  The water treatment system 1a further includes an exhaust heat pipe section 22 that connects a plurality of devices D3 and D4 adjacent to each other, a second heat storage unit 24, and a second bypass pipe 25. Water also flows through the exhaust heat pipe section 22. The heat pump 3 is thermally connected to the endothermic piping section 2 at the connection portion 6 of the endothermic piping section 2, and can exchange heat with water flowing through the endothermic piping section 2. The heat pump 3 is thermally connected to a part of the exhaust heat piping section 22 at the connection portion 26, and can exchange heat with water flowing through the exhaust heat piping section 22. For this reason, heat quantity can be exchanged between the heat absorption piping section 2 and the exhaust heat piping section 22 via the heat pump 3.

  The heat pump 3 uses a vapor compression type in this embodiment. FIG. 1B is a partial detailed view of the heat pump 3 shown in FIG. The heat pump 3 includes an evaporator 3a that evaporates refrigerant such as ammonia, carbon dioxide, chlorofluorocarbons, and alternative chlorofluorocarbons such as R410A, a compressor 3b that compresses the refrigerant, a condenser 3c that condenses the refrigerant, And an expansion valve 3d for expanding these components, and these elements are arranged on the closed loop 3e in this order. The refrigerant undergoes a thermal cycle of evaporation, compression, condensation, and expansion while circulating in the closed loop 3e. The evaporator 3a is thermally connected to the endothermic piping section 2 at the connection portion 6, and heat QC is taken from the water flowing through the endothermic piping section 2 by the heat of vaporization when the refrigerant evaporates. The evaporated refrigerant is compressed by the compressor 3b and becomes a high-temperature and high-pressure gas phase. The refrigerant is then sent to the condenser 3c. The condenser 3c is thermally connected to the exhaust heat piping section 22 at the connection portion 26, and the condensation heat QH released during the condensation is given to the water flowing through the exhaust heat piping section 22. The condensed refrigerant is cooled under reduced pressure through the expansion valve 3d. Thus, during the operation of one cycle of the heat pump 3, the cooling of the heat absorption piping section 2 and the heating of the exhaust heat piping section 22 are performed.

  In addition to the vapor compression type, the heat pump 3 may be a thermoelectronic, chemical, adsorption or absorption heat pump.

  The 1st heat storage means 4 is provided in the downstream rather than the connection part 6 with the heat pump 3 of the heat absorption piping area 2, and stores at least one part of the cooled water temporarily. A general tank can be used as the first heat storage means 4. A first flow rate adjusting unit 11 is provided on the downstream side of the first heat storage unit 4. As the first flow rate adjusting means 11, a general flow rate adjusting valve can be used.

  The first bypass pipe 5 branches from the endothermic pipe section 2 on the upstream side of the connecting portion 6 and merges with the endothermic pipe section 2 on the downstream side of the first heat storage means 4. A three-way valve 8 is provided at the branch portion, and the flow rate ratio of the water flowing through the heat absorption pipe section 2 and the first bypass pipe 5 can be adjusted. Instead of the first flow rate adjusting means 11, a three-way valve may be provided at the junction of the first bypass pipe 5 and the heat absorption pipe section 2.

  A first temperature sensor 9 is provided on the downstream side of the junction with the first bypass pipe 5 in the heat absorption pipe section 2.

  The first control unit 10 adjusts the opening of the three-way valve 8 according to the temperature T2 of the water measured by the first temperature sensor 9, and controls the flow rate of water flowing into the first bypass pipe 5. At the same time, the first flow rate adjusting means 11 is adjusted to control the flow rate of water flowing out from the first heat storage means 4.

  The 2nd heat storage means 24 is provided in the downstream rather than the connection part 26 with the heat pump 3 of the exhaust heat piping section 22, and stores at least one part of the heated water temporarily. As the second heat storage means 24, a general tank can be used as in the first heat storage means 4. A second flow rate adjusting means 31 is provided on the downstream side of the second heat storage means 24. As the second flow rate adjusting means 31, a general flow rate adjusting valve can be used.

  The second bypass pipe 25 is branched from the exhaust heat pipe section 22 on the upstream side of the connection portion 26 and merges with the exhaust heat pipe section 22 on the downstream side of the second heat storage means 24. A three-way valve 28 is provided at the branch portion, and the flow rate ratio of the water flowing through the exhaust heat pipe section 22 and the second bypass pipe 25 can be adjusted. Instead of the second flow rate adjusting means 31, a three-way valve may be provided at the junction of the second bypass pipe 25 and the exhaust heat pipe section 22.

  A second temperature sensor 29 is provided on the downstream side of the junction with the second bypass pipe 25 in the exhaust heat pipe section 22.

  The second control unit 30 determines the flow rate of water flowing into the second bypass pipe 25 and outflow from the second heat storage means 24 in accordance with the water temperature T2 ′ measured by the second temperature sensor 29. To control the flow rate of water. The second control unit 30 can be configured as a common control unit with the first control unit 10.

  Next, the operation of the water treatment system 1a described above will be described. Here, as a simple example, water of temperature T1 ′ flows into the exhaust heat pipe section 22 at a constant flow rate, branches to the exhaust heat pipe section 22 and the second bypass pipe 25 by the three-way valve 28, and then joins. Consider a case where the hot water is supplied at a temperature T2 ′. The temperature T2 'is controlled so as to be a constant target temperature. On the other hand, it is assumed that the temperature T1 'varies with time. The amount of heat QH applied from the heat pump 3 is constant, and the heat exchange efficiency in the water treatment system 1a and the heat dissipation in the second heat storage means 24 are ignored.

  First, as an initial state, the three-way valve 28 is adjusted so that the inflow ratio into the exhaust heat pipe section 22 and the second bypass pipe 25 becomes a predetermined value. Here, for the sake of simplicity, it is assumed that there is no inflow into the second bypass pipe 25. The second flow rate adjusting means 31 of the second heat storage means 24 is in a state where no flow rate adjustment is performed, that is, a state where the entire amount of water passes through the second heat storage means 24 as it is. Thereafter, the heat pump 3 is started, water is supplied at the temperature T1 ', and the temperature T2' of the water at the outlet side is continuously measured by the second temperature sensor 29.

  When the temperature T2 'exceeds the target temperature, the following operation is performed. First, the three-way valve 28 is adjusted so that a part of the water flows into the second bypass pipe 25. However, only by this, the temperature of the water flowing through the exhaust heat pipe section 22 rises and only joins the water flowing through the second bypass pipe 25 and returns to the temperature T2 ', so the temperature T2' does not change. Therefore, the flow rate at the outlet side of the second heat storage unit 24 is reduced by the second flow rate adjustment unit 31 provided on the outlet side of the second heat storage unit 24, and the second flow rate adjustment unit 31 is passed through. Water and water that has passed through the second bypass pipe 25 are mixed. As a result, the same effect as when the total amount of heat given to the combined water is reduced can be obtained, and the temperature T2 'can be lowered and the temperature T2' can be controlled to the target temperature. As a result of the above operation, the second heat storage means 24 stores hot water, that is, the amount of heat.

  Next, consider a case where the temperature T2 'has dropped from the target temperature. In this case, since the amount of heat necessary for maintaining the temperature T2 ′ at the target temperature is insufficient, the second flow rate adjusting means 31 is controlled to control the flow rate flowing out from the second heat storage means 24. increase. If the temperature T2 'recovers to the target temperature on the way, this state is maintained. If the temperature T2 'does not reach the target temperature, the flow rate flowing out from the second heat storage means 24 is further increased. At this time, the storage amount of the second heat storage unit 24 may decrease. This means that the amount of heat stored in the second heat storage means 24 is released to compensate for the shortage of heat. In this way, it is possible to control the temperature T2 'to be the target temperature by giving water the amount of heat equal to or higher than the supply heat amount QH applied from the heat pump 3.

  FIG. 2 schematically shows what has been described above. 2A shows the relationship between time and temperature T1 ', and FIG. 2B shows the relationship between time and the amount of hot water stored in the second heat storage means 24. FIG. When the temperature T1 'is high, an excessive amount of heating is generated, so that the amount of hot water stored in the second heat storage unit 24 increases (that is, the amount of heat is stored). That is, the second storage means 24 can temporarily store a part of the heat amount that can be exchanged between the heat pump 3 and the exhaust heat pipe section 22. Depending on the temperature T <b> 1 ′, the total amount of heat exchangeable may be temporarily stored. When the temperature T1 'becomes lower, the amount of heating becomes insufficient, so the amount of hot water stored in the second heat storage means 24 decreases (that is, the amount of heat is consumed).

  The temperature T2 in the endothermic piping section 2 can be similarly controlled. When the temperature T1 on the inlet side is low, a part of the cooled and cooled water is stored in the first heat storage means 4, and when the temperature T2 is high, it is stored in the first heat storage means 4. The cold water that has been discharged is discharged and the water is cooled to the desired temperature. The first heat storage means 4 can temporarily store at least a part (that is, part or all) of the heat amount that can be exchanged between the heat pump 3 and the heat absorption pipe section 2. Although cold water is actually stored in the first heat storage means 4, this cold water can take heat from the water flowing through the heat absorption pipe section 2. Therefore, it can be said that the first heat storage means 4 stores a heat quantity for cooling.

  Since the heat pump 3 uses the heat of vaporization at the time of evaporation of the refrigerant and the heat of condensation at the time of condensation, the heat pump 3 can perform heat transfer regardless of the temperatures on the heat absorption side and the exhaust heat side. That is, heat transfer is possible even when the water temperature on the heat absorption side and the water temperature on the exhaust heat side are almost the same, or when the water temperature on the exhaust heat side is higher than the water temperature on the heat absorption side. In a water treatment system, unlike a power generation system, for example, an extreme temperature difference hardly occurs in the system, and it is difficult to effectively use a general heat exchanger. For this reason, a method of supplying cold water or the like for cooling and steam or the like for heating is generally used. However, in the present invention, since the heat pump 3 is used, the piping section to be cooled and the heating target are heated. Regardless of the temperature of the piping section, the necessary amount of heat can be transferred between them.

  As in the present embodiment, the energy efficiency can be greatly increased by combining the method of absorbing heat from one piping section and heating the other piping section with the heat in the water treatment system with the heat storage means. This point will be described with reference to FIG.

  FIG. 3A shows the required amount of heat for heating in the piping section that needs heating on the left side, and the required amount of heat absorption in the piping section that needs cooling on the right side. For the sake of simplicity, the required heating heat amount varies with time, and the required endothermic heat amount is constant regardless of time. A possible cause of fluctuations in the amount of heat required for heating in the water treatment system may be fluctuations in the raw water temperature between day and night.

  FIG.3 (b) has shown the case where the heat pump 3 is comprised according to the minimum value of required heating calorie | heat amount. Since the amount of heat QC is taken from the object to be cooled and transferred by the heat pump 3 to give the amount of heat QH to the object to be heated, the energy efficiency is increased as compared with the case where cooling and heating are individually performed. However, in this example, since the endothermic heat quantity QC is smaller than the necessary endothermic heat quantity, it is necessary to supplement the insufficient endothermic heat quantity QC 'with other cooling means, as shown in FIG. Similarly, it is necessary to supplement the insufficient heating heat quantity QH ′ with other heating means.

  FIG.3 (d) has shown the case where the heat pump 3 is comprised according to the average value of required heating calorie | heat amount. In this example, since the amount of heat transferred by the heat pump 3 is increased, the energy efficiency is further increased as compared with the case shown in FIG. However, in this example as well, the endothermic heat quantity QC is still smaller than the necessary endothermic heat quantity, and as shown in FIG. 3 (e), the insufficient endothermic heat quantity QC "needs to be supplemented by other cooling means. The heating heat quantity QH "of the minute must be supplemented by other heating means. Furthermore, the excessive amount of heat QH ′ ″ must be discarded, which causes a reduction in energy efficiency.

  FIG. 3F shows an example in which the excess heating heat quantity QH ′ ″ that was discarded in the example of FIG. 3D is stored, and the insufficient heating heat quantity QH ″ is supplemented with the excess heating heat quantity QH ′ ″. This example shows an ideal case where the excess heating heat quantity QH ′ ″ and the insufficient heating heat quantity QH ″ coincide with each other, and other heating means are used in combination for heating. There is no need. However, even if they do not coincide with each other, at least a part of the excessive heating heat quantity QH ′ ″ can be used as at least a part of the insufficient heating heat quantity QH ″, so that energy efficiency can be improved. The endothermic heat quantity QC "needs to be supplemented by other cooling means, but the energy utilization efficiency is the highest as a whole, and the energy efficiency can be greatly improved.

(Second Embodiment)
Referring to FIG. 4, in addition to the first embodiment, the water treatment system 1b of the second embodiment is connected to the first bypass pipe 5 from the first heat storage means 4 on the upstream side of the connecting portion 6. 1 has a first reflux pipe 15 for refluxing water to the endothermic pipe section 2 on the downstream side of the branch portion. The first reflux pipe 15 constitutes a circulation loop together with the heat absorption pipe section 2. In this circulation loop, heat absorption by the heat pump 3 can always be performed. The temperature of the cold water stored in the first heat storage means 4 may rise due to heat exchange with the surroundings. When the cooling capacity of the heat pump 3 has a margin, the excess cooling capacity can be maintained by recooling the water stored in the first heat storage means 4.

  A similar reflux pipe can be provided for the second heat storage means 24. Referring to FIG. 4, the second reflux pipe 35 for refluxing water to the exhaust heat piping section 22 upstream of the connection portion 26 of the exhaust heat piping section 22 and downstream of the branch portion of the second bypass pipe 25 is provided. Is provided. Since the temperature of the warm water stored in the second heat storage means 24 may decrease due to heat exchange with the surroundings, the water whose temperature has been decreased by the second reflux pipe 35 is reheated by the heat pump 3, The surplus heating capacity stored in the second heat storage means 24 can be maintained.

  In the second heat storage means 24, the outflow portion L to the second reflux pipe 35 is desirably located below the inflow portion H from the exhaust heat pipe section 22. In particular, the inflow portion H from the exhaust heat pipe section 22 is preferably provided at the top of the second heat storage means 24, and the outflow portion L to the second reflux pipe 35 is preferably provided at the bottom of the second heat storage means 24. . When the operation of the heat pump 3 is started in a state where water is stored in the second heat storage unit 24, the hot water heated by the heat pump 3 flows into the second heat storage unit 24 from the inflow portion H located on the upper side. Thereby, the cooler water stored in the second heat storage means 24 moves to the lower part. Since a state where high temperature water and low temperature water are stratified temporarily occurs in the second heat storage means 24, low temperature water is efficiently supplied from the second heat storage means 24 to the heat pump 3, and heating efficiency is increased. Can be increased.

(Third embodiment)
As in the first and second embodiments, the third embodiment is applied when heat is absorbed from one piping section and the other piping sections are heated by the heat, but has an intermediate loop. And differ from these embodiments. Referring to FIG. 5, the water treatment system 1 c includes a heat absorption pipe section 2 in which water flows and a heat pump 3, as in the first embodiment. In the present embodiment, the water treatment system 1 c has a first intermediate loop 12. The first intermediate loop 12 is thermally connected to a part of the endothermic piping section 2 and the heat pump 3 at connection portions 6 and 16, respectively. The first intermediate loop 12 is configured such that a first heat medium for transferring heat between the water flowing through the heat absorbing pipe section 2 and the heat pump 3 flows. The first heat medium is not particularly limited, and there is no need to use a highly corrosive fluid or a fluid that easily generates scale. If filled with CO ₂ to the first intermediate loop 12 can carry heat efficiently than when filled with water.

  The water treatment system 1 c has a first intermediate loop bypass pipe 14 that branches from the first intermediate loop 12 by a three-way valve 18 and that joins the first intermediate loop 12 downstream thereof. Specifically, the first intermediate loop bypass pipe 14 branches from the first intermediate loop 12 on the downstream side of the connection portion 16 on the heat pump 3 side along the direction in which the first heat medium flows, and the heat absorption pipe. The first intermediate loop 12 joins upstream of the connection portion 6 on the section 2 side. The first intermediate loop bypass pipe 14 is provided with third heat storage means 13 for temporarily storing at least a part of the first heat medium flowing through the first intermediate loop 12. A first flow rate adjusting means 11 is provided downstream of the third heat storage means 13 along the flow direction of the first heat medium.

  A first temperature sensor 9 is provided on the downstream side of the connection portion 6 with the first intermediate loop 12 in the heat absorption pipe section 2.

  The first control unit 10 includes a flow rate of the first heat medium flowing into the first intermediate loop bypass pipe 14 according to the temperature of the water measured by the first temperature sensor 9, and a third heat storage unit. 13 controls the flow rate of the first heat medium flowing out from 13.

  The water treatment system 1 c further includes an exhaust heat pipe section 22, a second intermediate loop 32, a fourth heat storage unit 33, and a second intermediate loop bypass pipe 34. The second intermediate loop 32 is thermally connected to a part of the exhaust heat pipe section 22 and the heat pump 3 at connection portions 26 and 36, respectively. The second intermediate loop 32 is configured such that a second heat medium for transferring heat between the water flowing through the exhaust heat pipe section 22 and the heat pump 3 flows. As a result, heat is exchanged between the heat absorption pipe section 2 and the exhaust heat pipe section 22 via the heat pump 3. The second heat medium that can be used can be considered in the same way as the first heat medium.

  The water treatment system 1c has a second intermediate loop bypass pipe 34 that branches from the second intermediate loop 32 by a three-way valve 38 and that joins the second intermediate loop 32 downstream thereof. Specifically, the second intermediate loop bypass pipe 34 branches from the second intermediate loop 32 on the downstream side of the connection portion 36 on the heat pump 3 side along the direction in which the second heat medium flows, and exhaust heat is discharged. The second intermediate loop 32 joins upstream of the connecting portion 26 on the piping section 22 side. The second intermediate loop bypass pipe 34 is provided with fourth heat storage means 33 for temporarily storing at least a part of the second heat medium flowing through the second intermediate loop 32. A second flow rate adjusting means 31 is provided on the downstream side of the fourth heat storage means 33 along the flow direction of the second heat medium.

  A second temperature sensor 29 is provided on the upstream side of the connection portion 26 with the second intermediate loop 32 in the exhaust heat pipe section 22.

  The second control unit 30 determines the flow rate of the second heat medium flowing into the second intermediate loop bypass pipe 34 according to the water temperature T2 ′ measured by the second temperature sensor 29, and the fourth heat. The flow rate of the second heat medium flowing out from the storage means 33 is controlled.

  Although the present embodiment includes two intermediate loops 12 and 32, one of the intermediate loops may be configured such that no intermediate loop is provided as in the first embodiment.

  By providing the first intermediate loop 12 and the second intermediate loop 32, restrictions on the installation location of the heat pump 3 may be relaxed. That is, when the heat pump 3 is away from the endothermic piping section 2 or the like, it is necessary to draw these piping sections to the heat pump 3. In water treatment systems, in general, many devices with large pressure loss such as membrane devices and ion exchange devices are installed, so it is important to suppress pressure loss. In the example of FIG. 5, for example, the endothermic piping section 2 is installed with the shortest pipe length, and the endothermic piping section 2 and the heat pump 3 may be connected by the first intermediate loop 12 having a small pressure loss. It is possible to suppress the pressure loss. This advantage is particularly great when the heat pump 3 is away from the endothermic piping section 2 or the like. Although not shown, the first intermediate loop 12 can be configured as a double or triple loop as necessary. The same applies to the second intermediate loop 32.

  Furthermore, although illustration is omitted, at least one of the first intermediate loop 12 and the second intermediate loop 32 may be thermally connected to a plurality of piping sections. For example, another piping section that needs to be heated may be provided along the second intermediate loop 32 and heated together with the exhaust heat piping section 22. Since the intermediate loop has few route restrictions, it is easy to simultaneously cool a plurality of piping sections and heat the plurality of piping sections simultaneously with a single heat pump.

  Next, the operation of the water treatment system 1c described above will be described. Here, as a simple example, consider a case where water at a temperature T1 'flows into the exhaust heat pipe section 22 at a constant flow rate and is supplied as hot water at a temperature T2'. The temperature T2 'is controlled so as to be a constant target temperature. On the other hand, it is assumed that the temperature T1 'varies with time. The amount of heat QH applied from the heat pump 3 is constant, and heat exchange efficiency in the water treatment system 1c and heat dissipation in the fourth heat storage means 33 are ignored. The second intermediate loop 32 is thermally connected to the heat pump 3, and the second heat medium flowing through the second intermediate loop 32 is heated by the heat pump 3 and exchanges heat with water flowing through the exhaust heat pipe section 22. And cooled.

  First, as an initial state, the three-way valve 38 is adjusted so that the inflow ratio to the second intermediate loop bypass pipe 34 becomes a predetermined value. Here, for the sake of simplicity, it is assumed that there is no flow into the second intermediate loop bypass pipe 34. The second flow rate adjusting means 31 provided on the outlet side of the fourth heat storage means 33 is kept closed. Thereafter, the heat pump 3 is started, water is supplied at the temperature T1 ', and the temperature T2' of the water at the outlet side is continuously measured by the second temperature sensor 29.

  When the temperature T2 'exceeds the target temperature, the following operation is performed. First, the three-way valve 38 is adjusted so that a part of the second heat medium flows into the second intermediate loop bypass pipe 34. As a result, the flow rate of the second heat medium circulating through the second intermediate loop 32 decreases, and the amount of heat given to water per unit time decreases. As a result, the temperature T2 'can be lowered and the temperature T2' can be controlled to be the target temperature. As a result of the above operation, the second heat medium 33, that is, the amount of heat, is stored in the fourth heat storage means 33.

  Next, consider a case where the temperature T2 'has dropped from the target temperature. In this case, since the amount of heat necessary to maintain the temperature T2 ′ at the target temperature is insufficient, the second flow rate adjusting means 31 is controlled to store the second heat stored in the fourth heat storing means 33. Two heat carriers are discharged at a predetermined flow rate. The flow rate to be discharged depends on the amount of heat that is insufficient, and can be determined based on the measurement result of the temperature T2 '. In this way, the amount of heat stored in the fourth heat storage means 33 can be released to compensate for the shortage of heat, so that the temperature T2 'can be controlled to be the target temperature.

  The same applies to the endothermic piping section 2. In the endothermic piping section 2, when the temperature T1 on the inlet side is low, a part of the first heat medium cooled and lowered in temperature is stored in the third heat storage means 13, and when the temperature T1 is high, the third heat storage section 13 stores the third. The low-temperature first heat medium stored in the heat storage means 13 is released to cool the water to a desired temperature.

(Fourth embodiment)
Referring to FIG. 6, the water treatment system 1 d is thermally connected to each of the endothermic pipe section 2 and the heat pump 3, and performs heat exchange between the water flowing through the endothermic pipe section 2 and the heat pump 3. And a third intermediate loop 17 through which one heat medium flows. The water treatment system 1d further includes third heat storage means 13 for temporarily storing at least a part of the first heat medium. The third intermediate loop 17 is partitioned into a first circulation loop 17a and a second circulation loop 17b with the third heat storage means 13 interposed therebetween. The first circulation loop 17 a is thermally connected to the endothermic piping section 2 at the connection portion 6, and the first heat medium is circulated through the third heat storage means 13. The second circulation loop 17 b is thermally connected to the heat pump 3 at the connection portion 16, and the first heat medium circulates through the third heat storage unit 13. The second circulation loop 17b includes a supply pipe 19a for supplying the first heat medium.

  Similarly, the water treatment system 1d is thermally connected to each of the exhaust heat piping section 22 and the heat pump 3, and is a second for exchanging heat between the water flowing in the exhaust heat piping section 22 and the heat pump 3. A fourth intermediate loop 37 in which the heat medium flows, and a fourth heat storage means 33 for temporarily storing at least a part of the second heat medium. The fourth intermediate loop 37 is partitioned into a third circulation loop 37a and a fourth circulation loop 37b with the fourth heat storage means 33 interposed therebetween. The third circulation loop 37 a is thermally connected to the exhaust heat pipe section 22 at the connection portion 26, and the second heat medium is circulated through the fourth heat storage means 33. The fourth circulation loop 37 b is thermally connected to the heat pump 3 at the connection portion 36 so that the second heat medium circulates through the fourth heat storage means 33. The fourth circulation loop 37b includes a supply pipe 39a for supplying the second heat medium.

  When the temperature T1 ′ on the inlet side of the exhaust heat pipe section 22 is high, a part of the heat of the second heat medium heated and heated is stored in the fourth heat storage means 33, and the temperature T1 ′ is When the temperature is low, the second flow rate adjusting means 31 is adjusted, and the high-temperature second heat medium stored in the fourth heat storage means 33 is released to heat the water to a desired temperature.

  When the temperature T1 on the inlet side of the endothermic piping section 2 is low, a part of the heat of the first heat medium cooled and cooled is stored in the third heat storage means 13, and when the temperature T1 is high The first flow rate adjusting means 11 is adjusted, and the low-temperature first heat medium stored in the third heat storage means 13 is released to cool the water to a desired temperature.

  In the fourth heat storage means 33, it is desirable that the outflow portion L to the fourth circulation loop 39 is located below the inflow portion H from the fourth circulation loop. In particular, the inflow portion H from the fourth circulation loop is located at the uppermost part of the fourth heat storage means 33, and the outflow portion L to the fourth circulation loop is located at the lower part of the fourth heat storage means 33. It is desirable. The reason is the same as in the third embodiment.

  As described above, in each embodiment of the present invention, when the amount of heat supplied from the heat pump 3 is greater than the amount of heat necessary for heating or cooling the piping section, this is stored by the heat storage means and necessary. This is effectively used when there is a shortage of heat. Therefore, even if there is a surplus of heat, there is no need to perform wasteful standby or suppression operation of the heat pump in order to cope with load fluctuations, while there is no need to increase the capacity of the heat pump in preparation for a shortage of heat.

  Next, a specific example of water treatment to which the water treatment system described above is applied will be described. The water treatment system to which the present invention is applied can be composed of various devices (units) such as an ultrapure water production device, a wastewater treatment device, and a wastewater collection device. However, it should be noted that the configurations of these apparatuses vary depending on the required water quality of pure water, the quality of raw water and waste water, and the examples shown below are only examples.

  Fig.7 (a) has shown an example of schematic structure of the ultrapure water manufacturing apparatus among water treatment systems. The temperature of the raw water varies depending on the installation location and season, but here it is assumed to be 15 ° C. In order to produce pure water, raw water is passed through the turbidity membrane 108 to remove suspended matters and the like, and after passing through the activated carbon tower 109, it is heated at the heating point 101 and sent to the RO membrane device 110. The reason for heating is that the standard design temperature of the reverse osmosis membrane used in the RO membrane device 110 is 25 ° C., and this heating step is unnecessary depending on the temperature of the raw water. The raw water exiting the RO membrane device 110 is subjected to ion component removal by the ion exchange device 111 and stored in the primary pure water tank 112. In order to regenerate the resin used in the ion exchange device 111, the ion exchange device 111 is provided with a chemical supply line. The alkaline chemical solution is heated at the heating point 127 and supplied to the ion exchange device 111, and the waste solution of the alkaline chemical solution is obtained. Is cooled at the cooling point 128 and then neutralized with the acid waste liquid in the neutralization tank 113. The waste liquid is cooled in the neutralization tank 113 as necessary even after neutralization.

  Pure water stored in the primary pure water tank 112 is converted into an ultraviolet oxidizer 114, a cartridge polisher device (non-regenerative ion exchange unit filled with mixed bed ion exchange resin) 115, and an ultrafiltration membrane (UF membrane) device 116. It is used at each use point 117. The pure water that has not been used is collected in the primary pure water tank 112 through the circulation loop 118, and the circulation operation is continued. At this time, since the temperature of the circulating pure water rises due to heat input from a pump (not shown), the pure water is cooled according to the temperature requirement at the use point 117. In this example, a cooling point 119 is provided on the inlet side of the ultraviolet oxidizer 114. On the other hand, high-temperature ultrapure water of about 60 to 80 ° C. may be required depending on the purpose of use. In this example, the high-temperature ultrapure water supply line 120 is branched from the pure water tank 112, and after being heated at the heating point 121, it passes through the ultraviolet oxidation device 122, the cartridge polisher device 123, and the ultrafiltration membrane device 124. And sent to the use point 125. The high-temperature ultrapure water that has not been used is cooled at the cooling point 126 before returning to the primary pure water tank 112.

  FIGS. 7B to 7E show examples of various wastewater treatment apparatuses. The waste water may be generated inside the water treatment system or may be generated outside the water treatment system. Further, the treated wastewater may be discharged as it is outside the water treatment system, or may be reused in the ultrapure water production apparatus shown in FIG. 7A (marked with * in the figure).

  FIG.7 (b) has shown the process which performs anaerobic treatment and aerobic treatment to waste_water | drain. The anaerobic treatment and the aerobic treatment are wastewater treatments using anaerobic microorganisms and aerobic microorganisms. In this example, the optimum temperature of the anaerobic treatment (methane fermentation) is 36 to 38 ° C. (medium temperature fermentation), 53 Since it is comparatively high with -55 degreeC (high temperature fermentation), it is necessary to heat beforehand. On the other hand, since the appropriate temperature for the aerobic treatment is about 30 ° C., it is necessary to cool the waste water after the anaerobic treatment. FIG. 7C shows an example in which only the aerobic treatment is performed, and the waste water is heated to about 30 ° C. which is the optimum temperature for the aerobic treatment.

  FIG. 7D shows a process for stripping waste water. The stripping treatment is a treatment for removing free ammonia from waste water by blowing steam or air into the free ammonia. In this treatment, since it is desirable that the wastewater is supplied at a relatively high temperature, a heating point is provided on the inlet side of the stripping device.

  After the above-described anaerobic treatment, aerobic treatment and stripping treatment are completed, it is not necessary to adjust the temperature of the waste water. However, in order to obtain the amount of heat required at other heating points, heat can be absorbed as needed from the wastewater that has undergone the above treatment. Therefore, a cooling point is provided on the outlet side of these devices in the sense that it is a point capable of absorbing heat. Moreover, you may utilize these points as a discharge destination of the heat | fever which absorbed heat with the heat pump as needed conversely.

  FIG. 7E shows a treatment system for wastewater collected from a system in which ultrapure water is used. Usable waste water includes, for example, relatively clean water such as pure water used for rinsing a wafer during semiconductor manufacturing. The waste water is mixed with hydrogen peroxide and then sent to the ultraviolet oxidizer 101 to mainly remove the TOC (total organic carbon) component in the waste water. Next, the waste water is cooled at the cooling point 102, the organic matter and odor components are removed by the activated carbon tower 103, and sent to the ion exchange device 104. In the ultraviolet oxidation apparatus 101, the waste water stays for several hours, and the temperature may rise considerably. Therefore, a cooling point 102 is provided on the outlet side of the ultraviolet oxidation apparatus 101.

  FIG. 8 shows an example in which the ultrapure water production apparatus explained in FIG. 7A and the waste water treatment system explained in FIG. 7E are configured as one water treatment system among the apparatuses explained above. . Refer to the above description for the individual elements.

  FIG. 9 shows a process in the case of performing hot water sterilization during maintenance of the water treatment system. Here, the treated water is softened (removal of Ca ions and Mg ions), treated with activated carbon to obtain raw water, and the raw water is passed through an RO membrane device and an ion exchange device (electric deionized water production device (EDI)). Later, an example of a system that performs filtering and UV oxidation is shown. Fig. 9 (a) shows an example of sterilizing activated carbon and RO membrane with hot water. Normally, a hot water source isolated from the line is connected to the line, and hot water is supplied from the hot water source by the route indicated by the broken line. The RO membrane device and the activated carbon tower are sterilized with hot water. When the treatment is completed, the hot water is cooled and drained. FIG. 9B shows an example in the case of hot water sterilizing the EDI, filter, and ultraviolet oxidizer. Usually, a hot water source (heating heat exchange) isolated from the line is connected to the line, and the hot water source is indicated by a broken line. Hot water is supplied by the route shown, and the EDI is hot water sterilized. When the treatment is completed, the hot water is cooled and drained.

  7 to 9, the piping sections to be heated and cooled are indicated by thick lines. However, as described above, in the water treatment system, various pipes to be heated and cooled regardless of normal operation or maintenance. An interval exists. The water treatment system of the present invention may be applied individually to heating and cooling target piping sections, or may be applied by appropriately combining a heating target piping section and a cooling target piping section.

(Example)
The following measurements were performed using a system having an intermediate loop shown in FIG. A tank with a capacity of 5 m ³ was used as the heat storage means, and a heat pump having a compressor power of 7.5 kW and a coefficient of performance of 4 (when heated) was used. The adjustment operation of the heat pump according to the load was not performed, and the amount of heat supplied was constant at 30 kW (= 7.5 kW × performance coefficient 4). Heat pump outlet temperature (tapping temperature) T4 was set to 65 ° C. The inlet temperature T1 of the heating target water in the exhaust heat piping section was assumed to vary depending on the time zone during the day, and the outlet temperature T2 was controlled to be 25 ° C. The discharge flow rate of the heat medium from the heat storage means was controlled based on the measurement result of the temperature sensor.

  The water inlet temperature T1 and outlet temperature T2 were as shown in Table 1.

  Table 2 shows changes in various parameters every two hours in the water treatment system at this time. In the table, “flow rate (L / h)” is the supply flow rate of water, which is a constant value of 6500 L / h. “Necessary heat amount (kW)” indicates the amount of heat necessary for heating water to 25 ° C., and fluctuates with time (ie, inlet temperature T1). The “over / under heat amount (kW)” is a difference between the heat supply amount of the heat pump and the necessary heat amount, and the case where the heat amount is excessive is positive and the case where it is insufficient is negative. “Storage heat amount (kWh)” is the amount of heat stored in the heat storage means. When there is a surplus in the amount of heat supplied by the heat pump of 30 kW, the heat is stored in the heat storage means. Therefore, if the surplus state continues, the amount of stored heat increases. FIG. 11A is a graph showing changes with time in excess or deficiency of heat in the examples.

  Table 3 shows changes in various parameters in the intermediate loop. The temperature T3 was assumed to be equal to the water outlet temperature T2. “First heat storage means water storage amount (L / h)” indicates the amount of heat medium stored in the heat storage means per hour, and “Heat storage means water discharge amount (L / h)” indicates heat per hour. It shows the amount of heat medium released from the storage means. On the other hand, “storage heat quantity (kWh)” in Table 2 is a cumulative value of the heat quantity accumulated so far in the heat storage means.

  In the embodiment, the “storage heat quantity (kWh)” gradually increases, and then gradually consumed as the temperature T1 decreases and finally becomes zero. Therefore, there was no need to make up for the shortage with other heat sources, and the total amount of heat required for heating was 720 kWh. The actual energy consumed was 180 kWh in terms of compressor power. The amount of heat supplied from the heat pump of 30 kW can be said to be the amount of heat that can be exchanged between the heat pump and the exhaust heat pipe section. Between 10:00 and 20:00, only a part of the heat quantity that can be exchanged is used for heat exchange, and the remaining heat quantity is temporarily stored in the heat storage means. From 22:00 to 8:00, the amount of heat temporarily stored in the heat storage means is used to compensate for the shortage of exhaust heat to the exhaust heat piping section.

(Comparative Example 1)
The same measurement was performed for the case where no heat storage means was provided in the apparatus configuration of the example. The results are shown in Table 4. FIG. 11B is a graph showing the change over time in the amount of heat in excess and deficiency in Comparative Example 1. “Supply heat quantity from other heat source (kW)” is a heat quantity to be supplemented by other means (boiler, etc.) when the heating heat quantity is insufficient, and negative when it is insufficient. In the first half, the amount of heat supplied by the heat pump exceeds the required amount of heat, so heat supply from other heat sources is unnecessary, but excess heat is discarded. In the second half, the heat supply from the heat pump is less than the required heat, so heat supply from other heat sources is required. All deficiencies need to be supplied from other heat sources. The amount of heat required for this was 90 kWh. If this amount of heat is supplied by a boiler, the total required energy is 270 kWh obtained by adding 90 kWh to 180 kWh (necessary energy for the heat pump). Therefore, it is possible to save the total required energy by providing the first heat storage means.

(Comparative Example 2)
The same measurement was performed using a configuration in which the heat pump was replaced with a heat source such as a boiler in the apparatus configuration of the example. The results are shown in Table 5. FIG. 11C is a graph showing the change over time in the amount of heat in excess and deficiency in Comparative Example 2. In this case, as in the example, the total required heat amount is 720 kWh, but the required energy is 720 kWh, which requires four times as much energy as in the example.

DESCRIPTION OF SYMBOLS 1a-1d Water treatment system 2 Endothermic piping section 3 Heat pump 4 1st heat storage means 5 1st bypass pipe 6, 16, 26, 36 Connection part 8, 18, 28, 38 Three-way valve 9 1st temperature sensor 10 1st control part 11 1st flow volume adjustment means 12 1st intermediate loop 13 1st heat storage means 14 Intermediate loop bypass pipe 22 Waste heat piping section 24 2nd heat storage means 25 2nd bypass pipe 29 1st 2 temperature sensors 30 second control unit 31 second flow rate adjusting means 32 second intermediate loop 33 second heat storage means 34 second intermediate loop bypass pipe

Claims (10)

A plurality of water treatment devices;
Connecting the plurality of water treatment devices adjacent to each other, a plurality of piping sections through which water flows, and
At least one of the piping sections is used as an endothermic piping section to absorb heat from the endothermic piping section, and the heat absorbed from the endothermic piping section is used as at least one other piping section as an exhaust heat piping section. A heat pump that exhausts heat,
Heat that temporarily stores at least part of the heat quantity that can be exchanged between the heat pump and the heat absorption pipe section, or at least part of the heat quantity that can be exchanged between the heat pump and the exhaust heat pipe section. Storage means;
A first heat storage means provided on the downstream side of the connection portion with the heat pump in the endothermic piping section;
A water treatment system comprising: a first bypass pipe that branches from the endothermic piping section upstream of the connecting portion and merges with the endothermic piping section downstream of the heat storage means. A plurality of water treatment devices;
Connecting the plurality of water treatment devices adjacent to each other, a plurality of piping sections through which water flows, and
At least one of the piping sections is used as an endothermic piping section to absorb heat from the endothermic piping section, and the heat absorbed from the endothermic piping section is used as at least one other piping section as an exhaust heat piping section. A heat pump that exhausts heat,
Heat that temporarily stores at least part of the heat quantity that can be exchanged between the heat pump and the heat absorption pipe section, or at least part of the heat quantity that can be exchanged between the heat pump and the exhaust heat pipe section. Storage means;
A first heat storage means provided on the downstream side of the connection portion with the heat pump in the endothermic piping section;
A first bypass pipe branched from the endothermic pipe section upstream of the connecting portion and joined to the endothermic pipe section downstream of the first heat storage means;
A first reflux pipe for refluxing water from the first heat storage means to the endothermic pipe section upstream of the connecting portion and downstream of the branch portion of the first bypass pipe; There is a water treatment system. Second heat storage means provided on the downstream side of the connection portion with the heat pump in the exhaust heat pipe section;
A second bypass pipe branched from the exhaust heat pipe section upstream of the connecting portion of the exhaust heat pipe section and joining the exhaust heat pipe section downstream of the second heat storage means; It has, The water treatment system of Claim 1 or 2 . Second heat storage means provided on the downstream side of the connection portion with the heat pump in the exhaust heat pipe section;
A second bypass pipe branched from the exhaust heat piping section upstream of the connection portion of the exhaust heat piping section and joined to the exhaust heat piping section downstream of the second heat storage means;
A second recirculation for recirculating water from the second heat storage means to the exhaust heat piping section upstream of the connection portion of the exhaust heat piping section and downstream of the branch portion of the second bypass pipe. The water treatment system according to claim 1 or 2 , comprising a pipe. Second heat storage means provided on the downstream side of the connection portion with the heat pump in the exhaust heat pipe section;
A second bypass pipe branched from the exhaust heat piping section upstream of the connection portion of the exhaust heat piping section and joined to the exhaust heat piping section downstream of the second heat storage means;
A second recirculation for recirculating water from the second heat storage means to the exhaust heat piping section upstream of the connection portion of the exhaust heat piping section and downstream of the branch portion of the second bypass pipe. A tube, and
In the second heat storage means, the outlet portion of the second reflux pipe is located lower than the inflow section from the heat pipe section, water treatment system according to claim 1 or 2. A plurality of water treatment devices;
Connecting the plurality of water treatment devices adjacent to each other, a plurality of piping sections through which water flows, and
At least one of the piping sections is used as an endothermic piping section to absorb heat from the endothermic piping section, and the heat absorbed from the endothermic piping section is used as at least one other piping section as an exhaust heat piping section. A heat pump that exhausts heat,
Heat that temporarily stores at least part of the heat quantity that can be exchanged between the heat pump and the heat absorption pipe section, or at least part of the heat quantity that can be exchanged between the heat pump and the exhaust heat pipe section. Storage means;
A first heat medium that is thermally connected to each of the endothermic piping section and the heat pump and configured to flow a first heat medium for transferring heat between water flowing through the endothermic piping section and the heat pump. An intermediate loop of
A first branching along the flow direction of the first heat medium branches at the downstream side of the connection portion with the heat pump of the first intermediate loop, and merges at the upstream side of the connection portion with the heat absorption pipe section. An intermediate loop bypass pipe,
A third heat storage means provided in the first intermediate loop bypass pipe and temporarily storing at least a part of the first heat medium flowing through the first intermediate loop ; Water treatment system. A plurality of water treatment devices;
Connecting the plurality of water treatment devices adjacent to each other, a plurality of piping sections through which water flows, and
At least one of the piping sections is used as an endothermic piping section to absorb heat from the endothermic piping section, and the heat absorbed from the endothermic piping section is used as at least one other piping section as an exhaust heat piping section. A heat pump that exhausts heat,
Heat that temporarily stores at least part of the heat quantity that can be exchanged between the heat pump and the heat absorption pipe section, or at least part of the heat quantity that can be exchanged between the heat pump and the exhaust heat pipe section. Storage means;
A third heat medium that is thermally connected to each of the endothermic piping section and the heat pump and configured to flow a first heat medium for transferring heat between water flowing through the endothermic piping section and the heat pump. An intermediate loop of
And third heat storage means for temporarily storing at least a part of the first heat medium,
The third intermediate loop is thermally connected to the endothermic pipe section, and the first circulation loop is configured to circulate the first heat medium via the third heat storage unit; A water treatment system comprising: a second circulation loop that is thermally connected to a heat pump and configured to circulate the first heat medium through the third heat storage means. A second heat medium that is thermally connected to each of the exhaust heat piping section and the heat pump and that transfers heat between the water flowing through the exhaust heat piping section and the heat pump flows. A second intermediate loop;
A second branching along the direction in which the second heat medium flows branches downstream from the connection portion with the heat pump of the second intermediate loop, and joins upstream from the connection portion with the exhaust heat pipe section. Intermediate loop bypass pipe of
A fourth heat storage means provided in the second intermediate loop bypass pipe and temporarily storing at least a part of the second heat medium flowing through the second intermediate loop. The water treatment system according to claim 6 or 7 . A second heat medium that is thermally connected to each of the exhaust heat piping section and the heat pump and that transfers heat between the water flowing through the exhaust heat piping section and the heat pump flows. A fourth intermediate loop;
And fourth heat storage means for temporarily storing at least part of the second heat medium,
The fourth intermediate loop is thermally connected to the exhaust heat pipe section, and a third circulation loop in which the second heat medium is circulated through the fourth heat storage means; the heat pump and is thermally connected, having a fourth circulation loop the second heat medium is made to circulate through said fourth heat storage means, according to claim 6 or 7 Water treatment system. A second heat medium that is thermally connected to each of the exhaust heat piping section and the heat pump and that transfers heat between the water flowing through the exhaust heat piping section and the heat pump flows. A fourth intermediate loop;
And fourth heat storage means for temporarily storing at least part of the second heat medium,
The fourth intermediate loop is thermally connected to the exhaust heat pipe section, and a third circulation loop in which the second heat medium is circulated through the fourth heat storage means; A fourth circulation loop thermally connected to the heat pump and adapted to circulate the second heat medium through the fourth heat storage means;
The water treatment system according to claim 6 or 7 , wherein in the fourth heat storage means, an outflow portion to the fourth circulation loop is located below an inflow portion from the fourth circulation loop. .

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