WO2012057098A1

WO2012057098A1 - Water treatment system and water treatment method

Info

Publication number: WO2012057098A1
Application number: PCT/JP2011/074473
Authority: WO
Inventors: 亮輔寺師; 良行高橋; 川田　和彦
Original assignee: オルガノ株式会社
Priority date: 2010-10-27
Filing date: 2011-10-25
Publication date: 2012-05-03
Also published as: CN103209928A; KR101577125B1; KR20130102088A; TW201238647A; CN103209928B; TWI533924B

Abstract

In order to improve the energy efficiency of a water treatment system and perform stable temperature control, this water treatment system includes: a plurality of devices (1, 2, 3, 4); a plurality of pipe sections (11, 12) through which water flows and which connect the plurality of pairs of adjacent devices; and a heat pump (21) which absorbs heat from a heat absorption pipe section with at least one pipe section (11) being the heat absorption pipe section, and exhausts heat absorbed from the heat absorption pipe section (11) to a heat exhaust pipe section with at least another pipe section (12) being the heat exhaust pipe section.

Description

Water treatment system and water treatment method

The present invention relates to a water treatment system and a water treatment method, and particularly to a water treatment system with low energy consumption.

A water treatment system such as a pure water production system is configured 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., there are some between the raw water tank and the deaeration tank in order to adjust the temperature of the treated water at the entrance point of the RO membrane device to a temperature in the vicinity of this. The heat exchanger 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 heat exchange 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 JP 2006-095479 A

Conventionally, when adjusting the temperature of water to be treated flowing in a water treatment system, it has been common to provide equipment such as a cooling tower and a boiler. However, such a system configuration has the following problems in terms of energy utilization efficiency and, in turn, environmental loads such as carbon dioxide emissions.

That is, the energy for heating and cooling is individually input at the target site for heating and cooling. 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 produced by heat energy input to the boiler, and heat of the hot water or steam is added to the heating target part. . 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. The total energy required for temperature adjustment is the sum of the energy required for each target part of heating and cooling.

In a water treatment system, it is generally difficult to use heat deprived from a cooling target part as heat applied to the heating target part. In some cases, such a process can be realized by a heat exchanger. To that end, it is necessary that the part to be cooled is on the high temperature side and the part to be heated is on the low temperature side. Moreover, efficient heat transfer cannot be achieved unless there is a considerable temperature difference between the high temperature side and the low temperature side. In the case of a water treatment system, many parts are controlled at a temperature close to room temperature, there is no large temperature difference, and the relationship that the part to be cooled is the high temperature side and the part to be heated is the low temperature side is not necessarily established. Absent. Therefore, the part which can use a heat exchanger efficiently is limited.

Unlike heat exchangers, heat pumps can transfer heat from a low temperature heat source to a high temperature heat source. However, the performance of a heat pump that uses an external heat source such as air heat varies greatly depending on external temperature conditions. For example, when heat is absorbed from air at a low temperature, the heat absorption efficiency is greatly reduced. Thus, the heat pump using an external heat source such as air heat is easily affected by the external temperature, and it is difficult to stably control the water temperature in the water treatment system. If the heat pump has an excessive capacity, it is possible to mitigate the effects of fluctuations in external temperature conditions, but it has a significant effect on cost.
The present invention has been made in view of such problems, and an object thereof is to provide a water treatment system and a water treatment method that are high in energy efficiency and capable of stable temperature control.

The water treatment system of the present invention connects a plurality of devices and a plurality of devices adjacent to each other, a plurality of pipe sections through which water flows, and at least one pipe section as an endothermic pipe section. A heat pump that absorbs heat and exhausts the heat absorbed from the endothermic piping section to the exhaust heat piping section using at least one other piping section as an exhaust heat piping section.

The heat pump can take heat away from the heat absorption target part and move the heat to the heat exhaustion target part. Therefore, in the water treatment system, when there is a part that needs heat absorption (cooling) (endothermic piping section) and a part that needs exhaust heat (heating) (exhaust heat piping section), use a heat pump to It is possible to transfer heat from the heat exhaust pipe section. Since the heat lost for cooling can be utilized for heating another part, energy efficiency is remarkably improved.

In addition, each of the endothermic piping section and the exhaust heat piping section is a temperature adjusting part and a stable heat source. That is, as described above, when one of heat absorption or exhaust heat is performed using an external heat source, the heat pump performance is easily affected by temperature fluctuations of the external heat source. When using external air as a heat source, if the outside air temperature is low, heat absorption is difficult and heat pump performance is reduced. Even when groundwater or seawater is used as a heat source, the temperature does not change as much as air, but the same problem occurs. On the other hand, in the case of the present invention, since the piping section in the water treatment system in which the water temperature is controlled is used as the heat source (heat absorption piping section or exhaust heat piping section), the temperature variation of the heat source hardly occurs. For this reason, the heat pump performance is not easily influenced by the external environment such as the outside air temperature or the seawater temperature, and it becomes possible to stably maintain a good heat pump performance. In the case of a heat pump using air as a heat source, defrosting is required when the outside air temperature drops to near 0 ° C. In addition, in the case of a heat pump using groundwater or seawater as a heat source, it is necessary to treat wastewater and take measures against corrosion. The present invention does not cause such a problem.

According to another embodiment of the present invention, there is provided a water treatment method using a water treatment system having a plurality of devices and a plurality of piping sections that connect a plurality of adjacent devices and through which water flows. Provided. This method uses a heat pump to absorb heat from an endothermic piping section using at least one piping section as an endothermic piping section, and exhaust heat from the endothermic piping section, using at least one other piping section as an exhaust heat piping section. Includes exhausting heat.

As described above, according to the present invention, it is possible to provide a water treatment system and a water treatment method that are high in energy efficiency and capable of stable temperature control.

It is a conceptual diagram which shows 1st and 2nd embodiment of the water treatment system of this invention. In the water treatment system shown in FIG. 1, it is a conceptual diagram which shows embodiment which provided the intermediate | middle loop. In the water treatment system shown in Drawing 1, it is a key map showing an embodiment in which a plurality of heat absorption piping sections were provided. In the water treatment system shown in Drawing 1, it is a key map showing an embodiment in which a plurality of heat absorption and exhaust heat piping sections were provided. In the water treatment system shown in Drawing 1, it is a key map showing an embodiment provided with auxiliary heating means. In the water treatment system shown in Drawing 1, it is a key map showing an embodiment provided with the 2nd heat pump. In the water treatment system shown in FIG. 1, it is a conceptual diagram which shows embodiment using a thermoelectronic heat pump. It is the schematic which shows an example of a structure of a water treatment system. It is the schematic which shows an example of a structure of a water treatment system. It is the schematic which shows an example of a structure of a water treatment system. It is the schematic which shows an example of a structure of a water treatment system. 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 line structure at the time of the hot water sterilization of a water treatment system. It is the schematic which shows the structure of a reference example. It is the schematic which shows the structure of an Example. It is the schematic which shows the structure of an Example. It is a diagram (Mollier diagram) for demonstrating the effect of the 2nd Embodiment of this invention. It is a conceptual diagram which shows one Example 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 3rd 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 to FIG. 14A and 14B. It is a schematic diagram which shows notionally the effect | action of the water treatment system shown to FIG. 14A and 14B. It is a schematic diagram which shows the energy utilization efficiency of the water treatment system shown to FIG. 14A and 14B, and another water treatment system. It is a schematic diagram which shows the energy utilization efficiency of the water treatment system shown to FIG. 14A and 14B, and another water treatment system. It is a schematic diagram which shows the energy utilization efficiency of the water treatment system shown to FIG. 14A and 14B, and another water treatment system. It is a schematic diagram which shows the energy utilization efficiency of the water treatment system shown to FIG. 14A and 14B, and another water treatment system. It is a schematic diagram which shows the energy utilization efficiency of the water treatment system shown to FIG. 14A and 14B, and another water treatment system. It is a schematic diagram which shows the energy utilization efficiency of the water treatment system shown to FIG. 14A and 14B, and another water treatment system. It is a conceptual diagram which shows 4th Embodiment of the water treatment system of this invention. It is a conceptual diagram which shows 5th Embodiment of the water treatment system of this invention. It is a conceptual diagram which shows 6th Embodiment of the water treatment system of this invention. It is the schematic which shows the structure of the water treatment system of an Example. It is a graph which shows the time-dependent change of the excess and deficient heat amount of an Example. It is a graph which shows a time-dependent change of the excess and deficient heat amount of a comparative example. It is a graph which shows the time-dependent change of the required calorie | heat amount of a comparative example.

(First embodiment)
A first embodiment of the water treatment system of the present invention will be described with reference to FIGS. These figures extract and show only the part relevant to this embodiment among various apparatuses which comprise a water treatment system. An example of an actual water treatment system will be described later.

FIG. 1 shows first and

second devices

1 and 2 that are adjacent to each other, and a first piping section (heat absorption piping section) 11 that connects them. In these

devices

1 and 2 and the piping section 11, fluid (treated water) flows from the first device 1 to the second device 2 in the right direction in the figure. Similarly, FIG. 1 shows third and

fourth devices

3 and 4 that are adjacent to each other, and a second piping section (exhaust heat piping section) 12 that connects them. Also in these

devices

3 and 4 and the piping section 12, a fluid (treated water) flows from the third device 3 to the fourth device 4 in the right direction in the drawing. The first to fourth devices 1 to 4 may be any type.

In the present embodiment, heat is absorbed from the first piping section 11 (indicated by the symbol Q _C1 ) and is exhausted to the second piping section 12 (also indicated by the symbol Q _H1 ). In such a situation, for example, the outlet water temperature of the first device 1 is higher than the required water temperature at the inlet point of the second device 2, and it is necessary to cool the water to be treated, and the third device 3. This occurs when the outlet water temperature is lower than the required water temperature at the inlet point of the fourth apparatus 4 and it is necessary to heat the water to be treated. As an example, as described above, the RO membrane device has a standard design temperature of the reverse osmosis membrane of 25 ° C. If the water temperature at the inlet point is lower than this, it is necessary to heat the water to be treated before entering the RO membrane device. is there.

For this purpose, the water treatment system is provided with a heat pump 21 that absorbs heat from the first piping section 11 (endothermic piping section) and exhausts heat to the second piping section 12 (exhaust heat piping section). The heat pump 21 is thermally connected to the first piping section 11 and the second piping section 12. The heat pump 21 uses a vapor compression type in this embodiment. Specifically, the heat pump 21 includes an evaporator 22 that evaporates refrigerant such as ammonia, carbon dioxide, chlorofluorocarbons, and alternative chlorofluorocarbons such as R410A, a compressor 23 that compresses the refrigerant, and a condensation that condenses the refrigerant. And an expansion valve 25 for expanding the refrigerant. These elements 22 to 25 are arranged on the closed loop 26 in this order. Accordingly, the refrigerant undergoes a thermal cycle of evaporation, compression, condensation, and expansion while circulating in the closed loop 26. The first piping section 11 is located adjacent to the evaporator 22, and heat is taken away from the fluid flowing through the first piping section 11 by the heat of vaporization when the refrigerant evaporates (in each figure, The wavy line indicates the part where heat exchange takes place.) The evaporated refrigerant is compressed by the compressor 23 to become a high-temperature and high-pressure gas phase. The refrigerant is then sent to the condenser 24 where it releases heat and condenses. The second piping section 12 is located adjacent to the condenser 24, and the condensation heat released during the condensation is given to the fluid flowing through the second piping section 12. The condensed refrigerant passes through the expansion valve 25 and is cooled under reduced pressure. In this way, heat absorption from the first piping section 11 and exhaust heat to the second piping section 12 are performed during one cycle operation of the heat pump 21.

By using the heat pump 21, at least a part of the heat taken away from the first piping section 11 can be given to the second piping section 12. For this reason, it is not necessary to discard the deprived heat, and it is not necessary to generate heat supplied to the second piping section 12 by another device (boiler, etc.). In addition, the heat pump 21 generally has a coefficient of performance (defined as Q / L, where Q is the heating or cooling ability, and L is the power consumed to obtain this Q), and The required electrical energy is much smaller than the heat energy that is generated. Thus, in the water treatment system of this embodiment, since the heat deprived from the 1st piping section 11 is moved to the 2nd piping section 12, waste of heat energy does not arise easily. And since the heat pump 21 with high efficiency is used for this heat transfer, a small energy consumption is realized.

In addition, when a boiler and a cooling tower are separately installed for cooling and heating, these devices are generally provided at a location away from a site requiring temperature adjustment. This tendency is particularly strong in boilers that require a large number of incidental facilities such as fuel storage facilities. For this reason, the heat transfer loss at the time of transferring cold water, hot water, steam, etc. by piping is large, and it tends to be disadvantageous in terms of energy efficiency and cost, such as providing an additional heating and cooling device. In general, boilers and cooling towers require large energy and have a large environmental load. By installing the heat pump 21 in the vicinity of the middle between the first piping section 11 and the second piping section 12, heat transfer loss can be minimized.

Furthermore, the heat pump 21 can perform heat transfer regardless of the temperature 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. As described above, in a water treatment system, unlike a power generation system, for example, an extreme temperature difference does not often occur 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. In the present invention, since the heat pump 21 is used, the necessary amount of heat can be transferred between the first piping section 11 and the second piping section 12 regardless of the temperatures thereof.

As a usage form of the heat pump, a form using air or external water as a heat source is also conceivable. When air is used as a heat source, the second piping section 12 can be heated by absorbing heat from the air and exhausting the heat taken away from the air in the second piping section 12. However, when the air becomes cold, the heat pump has a lower endothermic efficiency, and the heat pump performance (coefficient of performance) is lowered. For this reason, when the driving | operation at low air temperature is assumed, it is necessary to increase the capacity | capacitance of a heat pump. Therefore, when the air temperature is high, it is necessary to operate with reduced performance. The same applies to cooling with a heat pump. In this case, if the outside air temperature is high, the exhaust heat efficiency decreases, and the heat pump capacity (coefficient of performance) decreases. Therefore, it is necessary to increase the capacity of the heat pump as well. Furthermore, when the outside air temperature is around 0 ° C., the air that has been deprived of heat is cooled to 0 ° C. or less, and thus there is a possibility that freezing will occur at the heat exchange site with the air. For this reason, it is necessary to take measures such as periodically stopping the operation and defrosting, or providing a separate defrosting facility, which is disadvantageous in terms of cost and operation.

A similar problem occurs when external water (seawater, groundwater, sewage, etc.) is used as a heat source. In the case of external water, the temperature fluctuation is not as great as that of air, and the temperature of groundwater is relatively stable, but it is still affected by the temperature fluctuation. When external water is used, a large amount of wastewater is generated, so that a large amount of equipment and cost may be required for the treatment. When discharging as sewage, the charge is also required. When a large amount of external water is required, there are restrictions on the location. Furthermore, when seawater is used, measures against scale, salt damage, and corrosion are required.

Furthermore, the use form of the heat pump that performs either endothermic or exhaust heat using an external heat source in this way is not different from conventional boilers and cooling towers in a broad sense. Because the efficiency of the heat pump itself is high, operating costs such as electricity bills can be reduced compared to boilers and cooling towers, but conversely, in order to cope with annual load fluctuations, an excessive capacity according to the peak load is provided. Because of this problem, application to water treatment systems is not realistic.

In contrast, in the present embodiment, the heat transfer is performed inside the water treatment system in which the temperature of the heat source is stable, and thus is not easily affected by the external environment. However, as will be described later, it is also effective to use air as the heat source when the heat source is in the range of normal temperature and temperature fluctuation is limited. Actually, there is almost no balance between the required heat absorption amount and the required exhaust heat amount, so an external heat source is used to adjust the excess or deficiency of the heat amount. However, the use of an external heat source is kept to a minimum and heat transfer is performed inside the system as much as possible, so that economical and stable temperature control is possible compared to the conventional case.

FIG. 2 also shows a system similar to FIG. In the present embodiment, a first intermediate loop 15 that transmits heat absorption from the first piping section 11 to the heat pump 21 is provided between the first piping section 11 and the heat pump 21. Similarly, a second intermediate loop 16 that transmits heat absorption from the heat pump 21 to the second piping section 12 is provided between the second piping section 12 and the heat pump 21. By providing the

intermediate loops

15 and 16 in this manner, restrictions on the installation location of the heat pump 21 may be relaxed. That is, when the heat pump 21 is away from the first piping section 11 and the second piping section 12, it is necessary to draw these piping

sections

11 and 12 to the heat pump 21. 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. 2, the first and

second piping sections

11 and 12 connect the first device 1 and the second device 2, the third device 3 and the fourth device 4 with the shortest distance, respectively. Since it is only necessary to connect the first and

second piping sections

11 and 12 and the heat pump 21 with the

intermediate loops

15 and 16 having a small pressure loss, it is possible to suppress the pressure loss of the water treatment system. This advantage is particularly great when the heat pump 21 is away from the first piping section 11 and the second piping section 12. Although illustration is omitted, only one of the first intermediate loop 15 and the second intermediate loop 16 may be provided, and each

intermediate loop

15, 16 is configured as a double or triple loop as necessary. It is also possible to do. The medium used for the intermediate loop 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

intermediate loop

15 and 16, it can carry heat efficiently than when filled with water.

FIGS. 3 and 4 show an embodiment of a water treatment system that absorbs heat or exhausts heat from a plurality of parts. Referring to FIG. 3, the water treatment system includes fifth and sixth devices 5, 6 adjacent to each other and a third piping section 13 (heat absorption piping section) connecting them, to which a fluid flows. And a first intermediate loop 15 adapted to absorb heat from the first and third piping sections 11 and 13. Referring to FIG. 4, in addition to the above-described configuration, the water treatment system includes seventh and

eighth devices

7 and 8 adjacent to each other, in which fluid is allowed to flow, and a fourth piping section 14 (drainage) connecting them. Thermal piping section) and a second intermediate loop 16 adapted to exhaust heat to the second and fourth piping sections 12 and 14.

As shown in these embodiments, the heat transfer side and the exhaust heat side are not limited to one piping section for transferring heat, and may be a plurality of positions. That is, the heat absorption pipe section and the exhaust heat pipe section can be any combination of single to single, single to multiple, multiple to single, and multiple to multiple. Since a plurality of piping sections are connected to one heat pump 21 via an intermediate loop, the number of heat pumps can be reduced. A plurality of intermediate loops and a plurality of heat pumps can also be provided in the water treatment system in consideration of the positional relationship between individual heat absorption and exhaust heat piping sections, the amount of moving heat, and the like.

Compressor capacity generally heat pump 21, heat absorption (cooling) and the required compressor capacity C _H corresponding to discharged heat amount (heat) in the corresponding required compressor capacity C _C and the exhaust heat pipe section to match the endothermic pipe section There is nothing, and it is decided according to either. Specifically, the following four patterns can be considered.
(Pattern 1) When C _H > C _C and the compressor capacity is C _H according to the exhaust heat (heating) side. In this case, since the heat absorption (cooling) in the endothermic piping section becomes excessive, the endothermic piping section is heated. Alternatively, in order to prevent excessive heat absorption (cooling) in the endothermic piping section, a part of the heat is taken from the endothermic piping section and the rest is taken out of the system (for example, taking the heat from the surrounding air and cooling the surrounding air) .) In other words, this also means that excessive cooling energy is released out of the system.
(Pattern ₂₎ a C H> _{C C,} when the _{C C} combined compressor capacity endothermic (cooling) side. In this case, since the exhaust heat (heating) in the exhaust heat piping section is insufficient, the exhaust heat piping section is additionally heated.
(Pattern 3) When C _H <C _C and the compressor capacity is C _H according to the exhaust heat (heating) side. In this case, since heat absorption (cooling) in the endothermic piping section is insufficient, heat is additionally removed from the endothermic piping section.
(Pattern ₄₎ a C H _{<C C,} when the _{C C} combined compressor capacity endothermic (cooling) side. In this case, since the exhaust heat (heating) in the exhaust heat piping section becomes excessive, heat is removed from the exhaust heat piping section. Or, in order to prevent the exhaust heat (heating) in the exhaust heat piping section from becoming excessive, part of the heat is exhausted to the exhaust heat piping section and the rest is exhausted outside the system (for example, heat is applied to the surrounding air to Heat the air.) In other words, this means that excess heating energy is released out of the system.

Thus, no matter what pattern is selected, it is necessary to remove or heat either the heat absorption piping section or the exhaust heat piping section, or to transfer heat to or from the outside of the water treatment system. Here, among these patterns, an example of pattern 2 in which exhaust heat (heating) in the exhaust heat piping section is insufficient and an example of pattern 1 in which heat absorption (cooling) in the heat absorption piping section is excessive are shown in FIG. , 6 will be described.

In the embodiment of FIG. 5, a second heat pump 27 that heats the second piping section 12 is provided to compensate for the shortage of exhaust heat (heating) from the heat pump 21 to the second piping section 12. . The basic configuration of the second heat pump 27 is the same as that of the heat pump 21, but the compressor capacity is appropriately set according to the amount of heat exhausted. In the present embodiment, the second heat pump 27 is used as a heater. The heat pump 21 takes the heat quantity Q _C1 from the first piping section 11 and releases the heat quantity Q _H1 to the second piping section 12. Here, the amount of heat _{Q C1} is the product of the coefficient of performance COP _C during compressor capacity _{C C} and the heat absorption, heat _{Q H1} is a value obtained by adding the compression work W of the compressor to the amount of heat _{Q C1.} That is, Q _C1 = C _C × COP _C , Q _H1 = Q _C1 + W, and the coefficient of performance COP _H = Q _H1 / W = Q _C1 / W + 1 = COP _C +1 during exhaust heat. That is, in principle, the amount of heat Q _H1 is larger than the amount of heat Q _C1 by the compression work W of the compressor, and COP _H is larger than COP _C by 1. The second pump 27 providing a heat Q2 of the difference between the heat quantity _{Q H1} and heat _{Q C1} applied to the second pipe 12 to the second pipe 12. Since the heat absorption side of the heat pump 27 is not connected to the water treatment system, the amount of heat Q2 is taken from the atmosphere (the atmosphere is cooled).

In the embodiment of FIG. 6, in order to compensate for excessive heat absorption from the first piping section 11 by the heat pump 21, the heat pump 21 includes a water heat exchange unit 21a and an air heat exchange unit 21b. The heat pump 21 is a water heat exchanging part 21 a that takes the heat quantity Q _C1 from the first piping section 11 (internal circulation water) and releases the heat quantity Q _H1 to the second piping section 12. The amount of heat Q _H1 given to the second piping section 12 matches the desired amount of heat. The air heat exchanging part 21 b takes away the amount of heat Q 2, which is the difference between the amount of heat QC ₁ and the amount of heat absorbed from the first piping section 11, and supplies it to the second piping section 12. In other words, the heat pump 21 takes heat from the first piping section 11 and the atmosphere. Since this embodiment does not require the second heat pump 27, it is often more advantageous than the embodiment of FIG. 5 from the viewpoint of cost.

The heat pump 21 can use a thermoelectronic type in addition to a vapor compression type. FIG. 7 shows an embodiment using a thermoelectric heat pump 21 '. The drawing is the same as FIG. 1 except that the vapor compression heat pump 21 shown in FIG. 1 is replaced with a thermoelectric heat pump 21 ′. For the description other than the heat pump 21 ′, refer to the above description. The thermoelectronic heat pump 21 ′ is a heat pump using the principle of a so-called thermoelectric element (Peltier element). A p-type semiconductor 29 and an n-type semiconductor 30 provided on the substrates 34 and 35 are connected in series via an electrode 33. When a current is passed through the pn junction, the n-type semiconductor 29 starts from the n-type along the direction of the current. An endothermic phenomenon occurs in the p-type junction 31, and a heat dissipation phenomenon occurs in the p-type to n-type junction 32. The p-type semiconductor 29 and the n-type semiconductor are arranged such that the junction portion 31 from the n-type to the p-type is on the first piping section 11 side and the junction portion 32 from the p-type to the n-type is on the second piping section 12 side. 30 is arranged. In FIG. 7, three p-type semiconductors 29 and three n-type semiconductors 30 are shown, but a larger number of p-type and n-type semiconductors may be alternately arranged. The thermoelectric heat pump 21 'has a simple structure and has no mechanical operation part, and therefore has excellent silence. The thermoelectric heat pump 21 'is preferably used as a small heat pump.

Furthermore, although not shown, it is also possible to use a chemical, adsorption or absorption heat pump. For example, a chemical heat pump includes a reaction chamber filled with a hydrate such as calcium chloride and calcium oxide, and a condensing chamber connected to the reaction chamber via a communication pipe. The first piping section 11 is positioned adjacent to the reaction chamber, and the second piping section 12 is positioned adjacent to the condensation chamber. Hydrate such as calcium chloride filled in the reaction chamber absorbs heat from the first piping section 11, whereby water molecules of the hydrate are separated from the hydrate as water vapor and transferred to the condensation chamber. The water vapor transferred to the condensing chamber is condensed and liquefied, and exhausted to the second piping section 12 located adjacent thereto.

Next, a specific example of water treatment to which the heat pump 21 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. The examples shown in FIGS. 8A-10B can be combined with water treatment systems according to all embodiments of the present invention.

FIG. 8A shows an example of a schematic configuration of an ultrapure water production apparatus in the water treatment system. 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. The standard design temperature of 25 ° C. is provided from the viewpoint of securing the amount of permeate and preventing salt adhesion. The water temperature at the outlet of the RO membrane device 110 is desirably in a range between about 25 ° C. and about 23 ° C. which is slightly lower than this. Depending on the temperature of the raw water, this heating step is unnecessary. 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. The water temperature on the inlet side of the ultraviolet oxidizer 114 is preferably about 20 to 30 ° C. 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. Since the ion exchange resin in the cartridge polisher device 123 is vulnerable to high temperatures, it is more desirable to provide a heating point 121 ′ between the cartridge polisher device 123 and the ultrafiltration membrane device 124 instead of the heating point 121.

8B to 8E 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. 8A (* in the figure).

FIG. 8B shows a process for performing anaerobic treatment and aerobic treatment on waste water. Anaerobic treatment and aerobic treatment are wastewater treatments using anaerobic microorganisms and aerobic microorganisms respectively. In this example, the optimum temperature for anaerobic treatment (methane fermentation) is 36 to 38 ° C. (medium temperature fermentation), 53 Since it is relatively high, up to 55 ° C. (high temperature fermentation), it is necessary to warm it in advance. In the case of medium temperature fermentation, the temperature can be in the range of 30 to 35 ° C. 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. 8C shows an example in which only the aerobic treatment is performed, and the waste water is heated to about 20 to 30 ° C. which is the optimum temperature for the aerobic treatment.

FIG. 8D 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. The ammonia stripping treatment is more efficient as the pH is higher, and the optimum temperature is about 20 to 35 ° C.

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. 8E 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 TOC (total organic carbon) components 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. 9 shows an example in which the ultrapure water production apparatus described in FIG. 8A and the waste water treatment system described in FIG. 8E are configured as one water treatment system among the apparatuses described above. Refer to the above description for the individual elements.

10A and 10B show 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. 10A is an example in the case 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 a route indicated by a broken line. The apparatus and activated carbon tower are sterilized with hot water. When the treatment is completed, the hot water is cooled and drained. FIG. 10B is an example in the case of hot water sterilization of EDI, filter, and ultraviolet oxidation device. Normally, a hot water source (heating heat exchange) isolated from the line is connected to the line, and the route shown by the broken line from the hot water source Hot water is supplied and EDI is sterilized with hot water. When the treatment is completed, the hot water is cooled and drained. Hot water is cooled and drained. Since the blow water after heat sterilization (water flowing into the cooling heat exchanger) is high-temperature water, it can be used as a heat source for the heat pump.

In FIGS. 8A to 10B, the exhaust heat pipe section and the endothermic pipe section are indicated by bold lines. As described above, in the water treatment system, various exhaust heat pipe sections and An endothermic piping section exists.

Next, the water treatment system according to the first embodiment described above will be described in more detail by way of examples. 11A to 11C are schematic views showing the A part of FIG. FIG. 11A shows a case where the exhaust heat pipe section and the endothermic pipe section are heated and cooled by separate devices (for example, a heat exchanger) according to the prior art. In the following description, the flow rate of the fluid flowing through the exhaust heat piping section is 100 t / h (tons per hour), the water temperature before heating is 288 K, the temperature after heating is 298 K, and the flow rate of the fluid flowing through the heat absorption piping section is 100 t / h. The water temperature before cooling is 303K, and the temperature after cooling is 298K. The specific heat of water is 4.2 J / g · K.

When the required energy is obtained under the above conditions, the required energy in the exhaust heat pipe section is about 1.17 × 10 ³ kW, and the required energy in the heat absorption pipe section is about 5.8 × 10 ² kW, which is about 1 in total. .8 × 10 ³ kW of energy is required.

11B and 11C show a case where heat is absorbed from the heat absorption pipe section by the heat pump and exhausted to the exhaust heat pipe section according to the present embodiment, and corresponds to FIGS. In FIG. 11B, the capacity of the compressor of the heat pump 21 (indicated as HP1 in the figure) is determined based on the necessary heat removal amount on the heat absorption side, and the amount of heat that is insufficient on the exhaust heat side is determined as the second heat pump 27 (indicated as HP2 in the figure). It is the structure which supplements with. FIG. 11C is a configuration in which the capacity of the compressor 21 is determined based on the required heat amount on the exhaust heat side, and a part of heat is absorbed from the atmosphere on the heat absorption side. Here, the coefficient of performance of the

heat pumps

21 and 27 in the water temperature range of 15 ° C. to 25 ° C. is 5 for heating and 4 for cooling.

In the case of FIG. 11B (Example 1), the necessary compressor capacity to obtain the heat removal amount of about 5.8 × 10 ² kW required on the heat absorption side is about 1.46 × 10 ² kW. With this compressor capacity, an exhaust heat amount of about 7.3 × 10 ² kW is obtained on the exhaust heat side. The difference between the actual amount of exhaust heat of about 1.17 × 10 ³ required in heat removal side (about 4.4 × ¹⁰ 2 kW) is supplemented by a second heat pump 27. The required compressor capacity of the second heat pump is about 0.88 × 10 ² kW, and a total electric energy of about 2.3 × 10 ² kW is required. This is 1/7 of the comparative example (conventional example) shown in FIG. 11A.

Similarly, in the case of FIG. 11C (Example 2), the required compressor capacity for obtaining the required exhaust heat amount of about 1.17 × 10 ³ on the exhaust heat side is about 2.3 × 10 ² kW. With this compressor capacity, the heat absorption side is removed to a necessary heat removal amount of about 5.8 × 10 ² kW or more, but the surplus is used for air cooling. Therefore, the required electrical energy is about 2.3 × 10 ² kW, as in FIG. 11B.

As a reference example, in the case of FIG. 11A, when heating and cooling are performed using a heat pump, a necessary heating amount on the heating side is about 1.17 × 10 ³ and a heat removal amount necessary on the cooling side is about 5.8 ×. Each 10 ² kW is provided by a separate heat pump. The required compressor capacity of the heat pump on the heating side is about 2.3 × 10 ² kW, and the required compressor capacity of the heat pump on the cooling side is about 1.5 × 10 ² kW, so a total of about 3.8 × 10 ² kW of electricity Energy is required. Therefore, although it is more advantageous than the comparative example, the result showed that the energy consumption was more than 60% compared to the example. The above is summarized in Table 1.

(Second Embodiment)
Conventionally, the heat cycle of a heat pump is generally designed so as to take a large temperature difference between a high temperature state (during condensation) and a low temperature state (during evaporation). This is because the conventional water heating heat pump is an alternative to a boiler and is designed to discharge hot water like a boiler.

However, in general, in the water treatment system, the temperature of the water flowing through the inside is often maintained at around room temperature, and is not brought to an extremely high or low temperature. In the case of heating, the temperature is often controlled to be 20 to 35 ° C.

Furthermore, if the temperature difference of the refrigerant is large, it is necessary to increase the compression work of the compressor, which directly leads to an increase in operating cost. If the temperature difference of the refrigerant is large, the heat dissipation loss from the inside of the heat pump also increases. It is desirable that the temperature difference of the refrigerant is the minimum necessary.

In view of such problems, the second embodiment provides a water treatment system and a water treatment method that have high energy efficiency and can perform stable temperature control.

In this embodiment, a vapor compression heat pump is used as the heat pump 21. In this embodiment, in each example of the first embodiment shown in FIGS. 1 to 6, the outlet side of the heat pump 21 in the second piping section 12 (exhaust heat piping section) and the first piping section 11 (endothermic piping section). ) On the inlet side of the heat pump 21 is controlled within the above temperature range. That is, in the present embodiment, the second piping section 12 is located on the outlet side of the heat pump (more generally, the portion 131 where heat is transferred between the second piping section 12 and the vapor compression heat pump. The water temperature at the outlet side) is set to 20 to 35 ° C. When the heat pump is operated under such temperature conditions, the energy efficiency is dramatically increased.

FIG. 12 is a Mollier diagram showing the thermal cycle of the vapor compression heat pump. As described above, in the vapor compression heat pump, the refrigerant circulating inside undergoes a thermal cycle of evaporation, compression, condensation, and expansion. Specifically, in the section from point A to point B, the refrigerant exchanges heat with a fluid having a temperature higher than that of the refrigerant (the refrigerant is heated and the high temperature fluid is cooled) and evaporates. In the section from point B to point C, compression is performed by the compressor, and the temperature and pressure rise. In the section from point C to point D, heat exchange is performed with a fluid having a temperature lower than that of the refrigerant (the refrigerant is cooled and the low-temperature fluid is heated) to be condensed. In the section from point D to point A, the refrigerant expands while passing through the expansion valve and is depressurized. Refrigerant takes heat Q _C from the outside of the fluid at the point A at point B interval (cooling step), subjected to compression work W by the compressor from the point B in the section the point C, outside the section of the point D from point C Heat Q _H is applied to the fluid (heating process). The coefficient of performance during heating is Q _H / W, and the coefficient of performance during cooling is Q _C / W. Therefore, the smaller the W is, the higher the coefficient of performance is, and the energy efficiency is improved.

The cycle ABCD corresponds to the condensation temperature T2 and the evaporation temperature T1. On the other hand, the cycle ABC′D ′ corresponds to a higher condensing temperature T2 ′ than usual (the evaporation temperature T1 is constant), and Q _H increases to Q _H ′, but the compression work W also increases. Increase to W '. As is clear from the figure, since Q _H / W ≧ Q _H '/ W', the coefficient of performance during heating decreases as the condensation temperature increases. Similarly, since Q _C / W ≧ Q _C / W ′, when the condensation temperature increases, the coefficient of performance during cooling decreases.

As described above, to increase the coefficient of performance, it is effective to reduce the difference between the condensation temperature and the evaporation temperature as much as possible. By the way, in a water treatment system, the temperature of water does not fluctuate greatly in the system, but only fluctuates within a range of several tens of degrees from a temperature near normal temperature. Therefore, by setting the target water temperature of the water to be temperature controlled to around normal temperature, the difference between the refrigerant condensation temperature and the evaporation temperature can be suppressed. In many cases, the temperature of a heating point (for example, an RO membrane device) in a water treatment system is generally controlled in a range of about 20 to 35 ° C. Therefore, if the water temperature of a specific part is adjusted to be about 20 to 35 ° C., the difference between the condensation temperature and the evaporation temperature can be suppressed, and an operation with extremely high energy efficiency becomes possible.

Suppose that this point is supplemented, in general water heating or steam compression heat pumps for hot water supply, heat sources are roughly divided into water and air. In the case of water, cold water is mainly targeted. In the case of air, it is outside air. In addition to water, even if it is outside air, the contained water may freeze near 0 ° C. For this reason, the condensation temperature is higher than 0 ° C., and therefore the line AB cannot be moved practically downward in the vertical axis direction. On the other hand, the position of the line CD (C′D ′) is determined by the compression work of the compressor. By setting the water temperature at the outlet side of the vapor compression heat pump in the second piping section 12 to be lower than the conventional one, the condensation temperature T2 can be lowered, and as a result, the compression work of the compressor can be reduced. As a result, the coefficient of performance of the heat pump can be increased and the operation efficiency can be increased.

The temperature on the inlet side of the heat pump 21 in the endothermic piping section 11 (more generally, the inlet side of the portion 132 in the first piping section 11 where heat is transferred to and from the vapor compression heat pump) is 20 When it is set to ˜35 ° C., the difference between the condensation temperature and the evaporation temperature of the heat pump 21 may be reduced, and the energy efficiency can be further improved.

As described above, in any of the embodiments shown in FIGS. 1 to 6, when the second piping section 12 (or 14) is the temperature control target piping, the vapor compression of the second piping section 12 (or 14) is performed. What is necessary is just to make it the water temperature in the exit side of the site | part 131 in which heat | fever transfer is performed between a heat pump to be 20-35 degreeC.

Conventionally, even when an intermediate loop is provided, the medium used in the intermediate loop is often at a high temperature and the heat dissipation loss in the intermediate loop is large. In this embodiment, the temperature on the outlet side of the vapor compression heat pump is 20 to 35. Since the temperature is as low as ° C., the temperature of the medium can be kept low, and heat dissipation loss can be suppressed.

Next, the water treatment system according to the second embodiment described above will be described in more detail by way of examples. As shown in FIG. 13, the water flowing through the second piping section 12 so that the temperature at the outlet side of the vapor compression heat pump becomes 20 to 35 ° C. by the vapor compression heat pump provided with a compressor with an output of 1.5 kW. Was heated. In this embodiment, the

devices

3 and 4 are not provided, and air is used as a heat source. The water temperature at the inlet side of the heat pump water to be heated was 21 ° C., and the ambient air temperature was 23 ° C. The heat pump outlet side water temperature was changed by changing the flow rate of the water to be heated. At this time, the outlet water temperature, energy consumption, and coefficient of performance (COP) for each flow rate are as follows.

In conventional heat pumps, the heat pump outlet water temperature of the water to be heated is often set higher. On the other hand, COP is remarkably improved if the heat pump outlet side water temperature of the water to be heated is set lower. A particularly high COP was obtained in the temperature range of 20-35 ° C. This is probably because the difference between the condensation temperature and the evaporation temperature is small.

(Third embodiment)
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 at a temperature close to room temperature, and 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.

The third to sixth embodiments provide a water treatment system that can easily suppress an increase in heat pump capacity, and a water treatment method using the water treatment system.

Referring to FIG. 14A, the water treatment system 201a includes a first piping section 202 (heat absorption piping section) that connects a plurality of adjacent devices D1 and D2, and a part of the first piping section 202 and the thermal treatment. A heat pump 203, a first heat storage means 204, and a first bypass pipe 205. The first piping section 202 is an arbitrary piping section that requires cooling in the water treatment system. Although the first piping section 202 is normally configured to allow water to flow, any fluid including a liquid or gas other than water may flow.

The water treatment system 201a further includes a second piping section 222 (exhaust heat piping section) that connects a plurality of adjacent devices D3 and D4, a second heat storage means 224, and a second bypass pipe 225. have. The second piping section 222 is also configured to allow water to flow. The heat pump 203 is thermally connected to the first piping section 202 at the connection portion 206 of the first piping section 202, and can exchange heat with the water flowing through the first piping section 202. The heat pump 203 is thermally connected to a part of the second piping section 222 at the connection portion 226, and can exchange heat with the water flowing through the second piping section 222. For this reason, heat quantity can be exchanged between the first piping section 202 and the second piping section 222 via the heat pump 203.

The heat pump 203 uses a vapor compression type in this embodiment. FIG. 14B is a partial detailed view of the heat pump 203 shown in FIG. 14A. The heat pump 203 includes an evaporator 203a that evaporates refrigerant such as ammonia, carbon dioxide, chlorofluorocarbons, and alternative chlorofluorocarbons such as R410A, a compressor 203b that compresses the refrigerant, a condenser 203c that condenses the refrigerant, And an expansion valve 203d for expanding these components, and these elements are arranged on the closed loop 203e in this order. The refrigerant undergoes a thermal cycle of evaporation, compression, condensation, and expansion while circulating in the closed loop 203e. The evaporator 203a is thermally connected to the first piping section 202 at the connecting portion 206, and heat QC is taken from the water flowing through the first piping section 202 by the heat of vaporization when the refrigerant evaporates. The evaporated refrigerant is compressed by the compressor 203b and becomes a high-temperature and high-pressure gas phase. The refrigerant is then sent to the condenser 203c. The condenser 203c is thermally connected to the second piping section 222 at the connection portion 226, and the condensation heat QH released during the condensation is given to the water flowing through the second piping section 222. The condensed refrigerant is cooled under reduced pressure through the expansion valve 203d. In this way, the cooling of the first piping section 202 and the heating of the second piping section 222 are performed during one cycle operation of the heat pump 203.

The heat pump 203 may be a thermoelectric, chemical, adsorption, or absorption heat pump in addition to the vapor compression type.

The first heat storage means 204 is provided on the downstream side of the connection portion 206 with the heat pump 203 in the first piping section 202, and temporarily stores at least a part of the cooled water. As the first heat storage means 204, a general tank can be used. A first flow rate adjusting unit 211 is provided on the downstream side of the first heat storage unit 204. As the first flow rate adjusting means 211, a general flow rate adjusting valve can be used.

The first bypass pipe 205 is branched from the first piping section 202 on the upstream side of the connecting portion 206 and merges with the first piping section 202 on the downstream side of the first heat storage means 204. A three-way valve 208 is provided at the branch portion, and the flow rate ratio of the water flowing through the first piping section 202 and the first bypass pipe 205 can be adjusted. Instead of the first flow rate adjusting means 211, a three-way valve may be provided at the junction of the first bypass pipe 205 and the first piping section 202.

A first temperature sensor 209 is provided on the downstream side of the junction with the first bypass pipe 205 in the first piping section 202.

The first control unit 210 controls the flow rate of water flowing into the first bypass pipe 205 by adjusting the opening degree of the three-way valve 208 according to the water temperature T2 measured by the first temperature sensor 209. At the same time, the first flow rate adjusting means 211 is adjusted to control the flow rate of water flowing out from the first heat storage means 204.

The second heat storage means 224 is provided on the downstream side of the connection part 226 with the heat pump 203 in the second piping section 222, and temporarily stores at least a part of the heated water. As the second heat storage means 224, a general tank can be used in the same manner as the first heat storage means 204. A second flow rate adjusting means 231 is provided on the downstream side of the second heat storage means 224. A general flow rate adjusting valve can be used as the second flow rate adjusting means 231.

The second bypass pipe 225 branches from the second piping section 222 on the upstream side of the connecting portion 226 and joins with the second piping section 222 on the downstream side of the second heat storage means 224. A three-way valve 228 is provided at the branch portion, and the flow rate ratio of the water flowing through the second piping section 222 and the second bypass pipe 225 can be adjusted. Instead of the second flow rate adjusting means 231, a three-way valve may be provided at the junction of the second bypass pipe 225 and the second piping section 222.

A second temperature sensor 229 is provided on the downstream side of the junction with the second bypass pipe 225 in the second piping section 222.

The second controller 230 controls the flow rate of water flowing into the second bypass pipe 225 and outflow from the second heat storage means 224 according to the water temperature T2 ′ measured by the second temperature sensor 229. To control the flow rate of water. The second control unit 230 can be configured as a common control unit with the first control unit 210.

Next, the operation of the water treatment system 201a described above will be described. Here, as a simple example, water of temperature T1 ′ flows into the second piping section 222 at a constant flow rate, branches to the second piping section 222 and the second bypass pipe 225 by the three-way valve 228, and then merges. Let us consider a case where the hot water is supplied at the 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. In addition, the supply heat quantity QH applied from the heat pump 203 is constant, and heat exchange efficiency in the water treatment system 201a and heat radiation in the second heat storage unit 224 are ignored.

First, as an initial state, the three-way valve 228 is adjusted so that the inflow ratio to the second piping section 222 and the second bypass pipe 225 becomes a predetermined value. Here, for simplicity, it is assumed that there is no inflow into the second bypass pipe 225. The second flow rate adjusting unit 231 of the second heat storage unit 224 is in a state where the flow rate is not adjusted, that is, a state in which the total amount of water passes through the second heat storage unit 224 as it is. Thereafter, the heat pump 203 is activated, 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 229.

When the temperature T2 'exceeds the target temperature, the following operation is performed. First, the three-way valve 228 is adjusted so that a part of the water flows into the second bypass pipe 225. However, only by this, the temperature of the water flowing through the second piping section 222 rises, and only the water flowing through the second bypass pipe 225 joins and returns to the temperature T2 ', so the temperature T2' does not change. Therefore, the flow rate on the outlet side of the second heat storage unit 224 is reduced by the second flow rate adjustment unit 231 provided on the outlet side of the second heat storage unit 224 and passed through the second flow rate adjustment unit 231. Water and water that has passed through the second bypass pipe 225 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 224 stores hot water, that is, the amount of heat.

Next, consider a case where the temperature T2 'falls 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 231 is controlled so that the flow rate flowing out from the second heat storage means 224 is reduced. increase. If the temperature T2 'recovers to the target temperature on the way, this state is maintained. When the temperature T2 'does not reach the target temperature, the flow rate flowing out from the second heat storage unit 224 is further increased. At this time, the storage amount of the second heat storage means 224 may decrease. This means that the amount of heat stored in the second heat storage means 224 is released, and the shortage of heat is compensated. 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 203.

15A and 15B schematically show what has been described above. FIG. 15A shows the relationship between time and temperature T <b> 1 ′, and FIG. 15B shows the relationship between time and the amount of hot water stored in the second heat storage means 224. 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 means 224 increases (that is, the amount of heat is stored). That is, the second storage unit 224 can temporarily store a part of the heat quantity that can be exchanged between the heat pump 203 and the second piping section 222. 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 warm water stored in the second heat storage means 224 decreases (that is, the amount of heat is consumed).

The temperature T2 of the first piping section 202 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 204, and when the temperature T2 is high, it is stored in the first heat storage means 204. The cold water that has been discharged is discharged and the water is cooled to the desired temperature. The first heat storage means 204 can temporarily store at least a part (that is, part or all) of the heat amount that can be exchanged between the heat pump 203 and the first piping section 202. Although cold water is actually stored in the first heat storage means 204, this cold water can take heat from the water flowing through the first piping section 202. Therefore, it can be said that the first heat storage means 204 stores the amount of heat for cooling.

As in this embodiment, energy efficiency can be significantly increased by combining a method of absorbing heat from one piping section within the water treatment system and heating the other piping section with the heat with the heat storage means. This point will be described with reference to FIGS. 16A to 16F.

FIG. 16A shows the required amount of heat in the pipe section that needs heating on the left side, and the required endothermic heat amount in the pipe section that needs to be cooled 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. 16B shows a case where the heat pump 203 is configured according to the minimum value of the required heating heat amount. Since the amount of heat QC is taken from the object to be cooled and transferred by the heat pump 203 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 performed individually. However, in this example, since the endothermic heat quantity QC is smaller than the necessary endothermic heat quantity, as shown in FIG. 16C, it is necessary to supplement the insufficient endothermic heat quantity QC 'with other cooling means. Similarly, it is necessary to supplement the insufficient heating heat quantity QH ′ with other heating means.

FIG. 16D shows a case where the heat pump 203 is configured in accordance with the average value of the required heating heat amount. In this example, since the amount of heat transferred by the heat pump 203 is increased, the energy efficiency is further increased as compared with the case shown in FIG. 16B. However, even in this example, since the endothermic heat quantity QC is still smaller than the necessary endothermic heat quantity, as shown in FIG. 16E, the insufficient endothermic heat quantity QC ″ needs to be supplemented by other cooling means. The amount of heat QH "needs to be supplemented by other heating means. Furthermore, the excessive amount of heat QH ′ ″ must be discarded, which causes a reduction in energy efficiency.

FIG. 16F shows an example in which the excess heating heat quantity QH ′ ″ discarded in the example of FIG. 16D is stored, and the insufficient heating heat quantity QH ″ is supplemented with the excess heating heat quantity QH ′ ″. The example shows an ideal case where the excess heating heat quantity QH ′ ″ and the insufficient heating heat quantity QH ″ coincide with each other, and it is not necessary to use other heating means together for heating. 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.

(Fourth embodiment)
Referring to FIG. 17, in addition to the third embodiment, the water treatment system 201 b of the fourth embodiment is connected to the first bypass pipe 205 from the first heat storage unit 204 on the upstream side of the connection portion 206. The first reflux pipe 215 for refluxing water is provided in the first piping section 202 on the downstream side of the branch portion. The first reflux pipe 215 forms a circulation loop together with the first piping section 202. In this circulation loop, heat absorption by the heat pump 203 can always be performed. The temperature of the cold water stored in the first heat storage means 204 may increase due to heat exchange with the surroundings. When the cooling capacity of the heat pump 203 has a margin, the excess cooling capacity can be maintained by recooling the water stored in the first heat storage unit 204.

A similar reflux pipe can be provided for the second heat storage means 224 as well. Referring to FIG. 17, the second reflux pipe for refluxing water to the second pipe section 222 upstream of the connection portion 226 of the second pipe section 222 and downstream of the branch portion of the second bypass pipe 225. 235 is provided. Since the temperature of the warm water stored in the second heat storage means 224 may decrease due to heat exchange with the surroundings, the water whose temperature has been decreased by the second reflux pipe 235 is reheated by the heat pump 203. The surplus heating capacity stored in the second heat storage means 224 can be maintained.

In the second heat storage means 224, the outflow portion L to the second reflux pipe 235 is preferably located below the inflow portion H from the second piping section 222. In particular, the inflow portion H from the second piping section 222 is provided at the top of the second heat storage means 224, and the outflow portion L to the second reflux pipe 235 is provided at the bottom of the second heat storage means 224. desirable. When the operation of the heat pump 203 is started in a state where water is stored in the second heat storage means 224, the hot water heated by the heat pump 203 flows into the second heat storage means 224 from the inflow portion H located on the upper side. Thereby, the cooler water stored in the second heat storage means 224 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 224, low temperature water is efficiently supplied from the second heat storage means 224 to the heat pump 203, and the heating efficiency Can be increased.

(Fifth embodiment)
As in the third and fourth embodiments, the fifth embodiment is applied when heat is absorbed from one pipe section and the other pipe sections are heated by the heat, but has an intermediate loop. And differ from these embodiments. Referring to FIG. 18, the water treatment system 201 c includes a first piping section 202 in which water flows and a heat pump 203, as in the first embodiment. In the present embodiment, the water treatment system 201 c has a first intermediate loop 212. The first intermediate loop 212 is thermally connected to a part of the first piping section 202 and the heat pump 203 at

connection portions

206 and 216, respectively. The first intermediate loop 212 is configured such that a first heat medium for transferring heat between water flowing through the first piping section 202 and the heat pump 203 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 212, it can carry heat efficiently than when filled with water.

The water treatment system 201c has a first intermediate loop bypass pipe 214 that branches from the first intermediate loop 212 by a three-way valve 218 and joins the first intermediate loop 212 downstream thereof. Specifically, the first intermediate loop bypass pipe 214 branches from the first intermediate loop 212 on the downstream side of the connection part 216 on the heat pump 203 side along the direction in which the first heat medium flows, The first intermediate loop 212 is joined upstream of the connecting portion 206 on the piping section 202 side. The first intermediate loop bypass pipe 214 is provided with third heat storage means 213 for temporarily storing at least a part of the first heat medium flowing through the first intermediate loop 212. A first flow rate adjusting unit 211 is provided downstream of the third heat storage unit 213 along the flow direction of the first heat medium.

The first temperature sensor 209 is provided on the downstream side of the connecting portion 206 with the first intermediate loop 212 in the first piping section 202.

The first control unit 210 includes a flow rate of the first heat medium flowing into the first intermediate loop bypass pipe 214 according to the temperature of the water measured by the first temperature sensor 209, and a third heat storage unit. The flow rate of the first heat medium flowing out from 213 is controlled.

The water treatment system 201 c further includes a second piping section 222, a second intermediate loop 232, a fourth heat storage unit 233, and a second intermediate loop bypass pipe 234. The second intermediate loop 232 is thermally connected to a part of the second piping section 222 and the heat pump 203 at

connection portions

226 and 236, respectively. The second intermediate loop 232 is configured such that a second heat medium for transferring heat between water flowing through the second piping section 222 and the heat pump 203 flows. As a result, heat is exchanged between the first piping section 202 and the second piping section 222 via the heat pump 203. The second heat medium that can be used can be considered in the same way as the first heat medium.

The water treatment system 201 c has a second intermediate loop bypass pipe 234 that branches from the second intermediate loop 232 by the three-way valve 238 and merges with the second intermediate loop 232 downstream thereof. Specifically, the second intermediate loop bypass pipe 234 branches from the second intermediate loop 232 on the downstream side of the connection part 236 on the heat pump 203 side along the direction in which the second heat medium flows. The second intermediate loop 232 joins upstream of the connecting portion 226 on the piping section 222 side. The second intermediate loop bypass pipe 234 is provided with fourth heat storage means 233 for temporarily storing at least a part of the second heat medium flowing through the second intermediate loop 232. A second flow rate adjusting means 231 is provided downstream of the fourth heat storage means 233 along the flow direction of the second heat medium.

A second temperature sensor 229 is provided on the upstream side of the connection portion 226 with the second intermediate loop 232 in the second piping section 222.

The second controller 230 controls the flow rate of the second heat medium flowing into the second intermediate loop bypass pipe 234 in accordance with the water temperature T2 ′ measured by the second temperature sensor 229, and the fourth heat. The flow rate of the second heat medium flowing out from the storage means 233 is controlled.

Although the present embodiment includes two

intermediate loops

212 and 232, one intermediate loop may be configured not to have an intermediate loop as in the first embodiment.

By providing the first intermediate loop 212 and the second intermediate loop 232, restrictions on the installation location of the heat pump 3 may be relaxed. That is, when the heat pump 203 is away from the first piping section 202 and the like, it is necessary to draw these piping sections to the heat pump 203. 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. 18, for example, the first piping section 202 is installed with the shortest piping length, and the first piping section 202 and the heat pump 203 may be connected by the first intermediate loop 212 with a small pressure loss. It is possible to suppress the pressure loss of the water treatment system. This advantage is particularly great when the heat pump 3 is away from the first piping section 202 and the like. Although not shown, the first intermediate loop 212 can be configured as a double or triple loop as necessary. The same applies to the second intermediate loop 232.

Further, although not shown, at least one of the first intermediate loop 212 and the second intermediate loop 232 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 232 and heated together with the second piping section 222. 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 201c described above will be described. Here, as a simple example, consider a case where water at a temperature T1 'flows into the second piping section 222 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 203 is constant, and the heat exchange efficiency in the water treatment system 201c and the heat dissipation in the fourth heat storage means 233 are ignored. The second intermediate loop 232 is thermally connected to the heat pump 203, and the second heat medium flowing through the second intermediate loop 232 is heated by the heat pump 203 and heat and water flowing through the second piping section 222. Replace and cool.

First, as an initial state, the three-way valve 238 is adjusted so that the inflow ratio to the second intermediate loop bypass pipe 234 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 234. The second flow rate adjusting means 231 provided on the outlet side of the fourth heat storage means 233 is kept closed. Thereafter, the heat pump 203 is activated, 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 229.

When the temperature T2 'exceeds the target temperature, the following operation is performed. First, the three-way valve 238 is adjusted so that a part of the second heat medium flows into the second intermediate loop bypass pipe 234. As a result, the flow rate of the second heat medium circulating in the second intermediate loop 232 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 fourth heat storage means 233 stores the heated second heat medium, that is, the amount of heat.

Next, consider a case where the temperature T2 'falls 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 231 is controlled to store the first heat stored in the fourth heat storage means 233. 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 233 can be released to compensate for the shortage of heat, so the temperature T2 'can be controlled to be the target temperature.

The same applies to the first piping section 202. In the first piping section 202, when the temperature T1 on the inlet side is low, a part of the first heat medium cooled and cooled is stored in the third heat storage means 213, and when the temperature T1 is high. The low-temperature first heat medium stored in the third heat storage means 213 is released to cool the water to a desired temperature.

(Sixth embodiment)
Referring to FIG. 19, the water treatment system 201d is thermally connected to each of the first piping section 202 and the heat pump 203, and exchanges heat between the water flowing through the first piping section 202 and the heat pump 203. It has a third intermediate loop 217 adapted to flow a first heat medium for performing. The water treatment system 201d further includes third heat storage means 213 that temporarily stores at least a part of the first heat medium. The third intermediate loop 217 is partitioned into a first circulation loop 217a and a second circulation loop 217b with the third heat storage means 213 interposed therebetween. The first circulation loop 217a is thermally connected to the first piping section 202 at the connection portion 206, and the first heat medium circulates through the third heat storage means 213. . The second circulation loop 217 b is thermally connected to the heat pump 203 at the connection portion 216, and the first heat medium circulates through the third heat storage unit 213. The second circulation loop 217b includes a supply pipe 219a for supplying the first heat medium.

Similarly, the water treatment system 201d is thermally connected to each of the second piping section 222 and the heat pump 203, and exchanges heat between the water flowing through the second piping section 222 and the heat pump 203. A fourth intermediate loop 237 in which the second heat medium flows is provided, and fourth heat storage means 233 that temporarily stores at least a part of the second heat medium. The fourth intermediate loop 237 is partitioned into a third circulation loop 237a and a fourth circulation loop 237b with the fourth heat storage means 233 interposed therebetween. The third circulation loop 237a is thermally connected to the second piping section 222 at the connection portion 226, and the second heat medium circulates through the fourth heat storage means 233. . The fourth circulation loop 237b is thermally connected to the heat pump 203 at the connection portion 236 so that the second heat medium circulates through the fourth heat storage means 233. The fourth circulation loop 237b includes a supply pipe 239a for supplying the second heat medium.

When the temperature T1 ′ on the inlet side of the second piping section 222 is high, a part of the heat of the second heat medium heated by the heating is stored in the fourth heat storage means 233, and the temperature T1 ′. Is low, the second flow rate adjusting means 231 is adjusted, the high-temperature second heat medium stored in the fourth heat storage means 233 is released, and the water is heated to a desired temperature.

When the temperature T1 on the inlet side of the first piping section 202 is low, a part of the heat of the first heat medium cooled and cooled is stored in the third heat storage means 213, and the temperature T1 is high. In this case, the first flow rate adjusting unit 211 is adjusted, and the low-temperature first heat medium stored in the third heat storage unit 213 is released to cool the water to a desired temperature.

In the fourth heat storage means 233, it is desirable that the outflow portion L to the fourth circulation loop 239 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 top of the fourth heat storage means 233, and the outflow portion L to the fourth circulation loop is located at the lower portion of the fourth heat storage means 233. It is desirable. The reason is the same as in the fifth embodiment.

As described above, in each of the third to sixth embodiments, when the amount of heat supplied from the heat pump 203 is greater than the amount of heat necessary for heating or cooling the piping section, this is stored in the heat storage means. However, this is effectively utilized when the required amount of heat is insufficient. 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.

(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 with 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.

Water inlet temperature T1 and outlet temperature T2 were as shown in Table 3.

Table 4 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. 21A is a graph showing changes with time in excess or deficiency of heat in the examples.

Table 5 shows changes in various parameters in the intermediate loop. The temperature T3 was assumed to be equal to the water outlet temperature T2. “Heat medium storage means water storage amount (L / h)” indicates the amount of heat medium stored in the heat storage means per hour, and “Heat medium means water discharge amount (L / h)” is the heat storage means per hour. The amount of the heat medium released from the is shown. On the other hand, “storage heat quantity (kWh)” in Table 4 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 8 o'clock and 20 o'clock, only a part of the heat exchangeable heat is used for heat exchange, and the remaining heat 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 6. FIG. 21B 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 7. FIG. 21C 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.

1 to 6 First to sixth devices 11, 13 First and third piping sections (endothermic piping sections)
12, 14 2nd and 4th piping section (exhaust heat piping section)
21, 21 ', 21 "heat pump 202 first piping section (endothermic piping section)
203 heat pump 204 first heat storage means 222 second piping section (exhaust heat piping section)
224 Second heat storage means

Claims

Multiple devices;
A plurality of piping sections that connect the plurality of adjacent devices, and through which water flows;
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,
Having a water treatment system.
In order to compensate for insufficient or excessive heat absorption from the endothermic piping section, or insufficient or excessive exhaust heat to the exhaust heat piping section, the endothermic piping section or the exhaust heat piping section is heated or removed. The water treatment system according to claim 1, further comprising means for heating or means for transferring heat to and from the outside of the water treatment system.
The water treatment system according to claim 2, wherein the means is a second heat pump.
Provided between the heat absorption piping section and the heat pump, provided between the first intermediate loop for transferring heat absorption from the heat absorption piping section to the heat pump, the exhaust heat piping section and the heat pump, The water treatment system according to claim 1, comprising at least one of second intermediate loops that transmits waste heat from the heat pump to the waste heat pipe section.
The heat absorption piping section is provided in a plurality of places, and a first intermediate loop that transmits heat absorption from the plurality of heat absorption piping sections to the heat pump is provided between the plurality of heat absorption piping sections and the heat pump. Water treatment system as described in.
A plurality of the exhaust heat piping sections are provided, and a second intermediate loop for transmitting the exhaust heat from the heat pump to the plurality of exhaust heat piping sections is provided between the plurality of exhaust heat piping sections and the heat pump. The water treatment system according to claim 1.
The water treatment system according to claim 1, wherein the heat pump is any one of a vapor compression type, an absorption type, an adsorption type, a thermoelectronic type, and a chemical type.
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. The water treatment system according to claim 1, comprising 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;
The first bypass pipe that branches from the endothermic pipe section upstream of the connecting portion and merges with the endothermic pipe section downstream of the heat storage means. Water treatment system.
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; The water treatment system according to claim 8.
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; The water treatment system according to claim 8, comprising:
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 8, 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
9. The water treatment system according to claim 8, wherein in the second heat storage unit, an outflow portion to the second reflux pipe is located below an inflow portion from the exhaust heat pipe section.
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; The water treatment system according to claim 8.
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 second circulation loop that is thermally connected to a heat pump and is configured to circulate the first heat medium through the third heat storage means. 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 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 8.
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 water treatment according to claim 8, further comprising: a fourth circulation loop thermally connected to the heat pump and configured to circulate the second heat medium through the fourth heat storage unit. 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;
9. The water treatment system according to claim 8, wherein in the fourth heat storage unit, an outflow portion to the fourth circulation loop is located below an inflow portion from the fourth circulation loop.
The heat pump is a vapor compression heat pump, and is configured such that the temperature of water at the outlet side of the portion where heat is transferred between the heat pumps in the exhaust heat pipe section is 20 to 35 ° C. The water treatment system according to claim 1.
The water treatment system according to claim 19, wherein the heat absorption pipe section is configured such that water having a temperature of 20 to 35 ° C flows on an inlet side of a portion where heat is exchanged with the heat pump.
The water treatment system according to claim 19, further comprising means for heating or cooling the exhaust heat pipe section or the heat absorption pipe section separately from the heat pump.
Between the exhaust heat piping section and the heat pump, or at least one of the heat absorption piping section and the vapor compression heat pump, between the exhaust heat piping section or the heat absorption piping section and the heat pump. The water treatment system according to claim 19, comprising an intermediate loop for transferring heat.
The water treatment system according to claim 19, wherein the heat pump heats the water flowing through the inlet-side piping section of the reverse osmosis membrane device so that the water temperature becomes 23 to 25 ° C.
The water treatment system according to claim 19, wherein the heat pump heats the water flowing through the inlet side piping section of the ultraviolet oxidizer so that the water temperature becomes 20 to 30 ° C.
The water treatment system according to claim 19, wherein the heat pump heats the water flowing in the inlet side piping section of the ammonia stripping device so that the water temperature becomes 20 to 35 ° C.
The water treatment system according to claim 19, wherein the heat pump heats the water flowing through the inlet side piping section of the aerobic treatment device so that the water temperature becomes 20 to 30 ° C.
A water treatment method using a water treatment system having a plurality of devices and a plurality of piping sections that connect the plurality of devices adjacent to each other and through which water flows,
The heat pump absorbs heat from the endothermic piping section using at least one of the piping sections as an endothermic piping section, and the exhaust heat piping uses the heat absorbed from the endothermic piping section as at least one other piping section. A water treatment method comprising exhausting heat to a section.
Passing water through an exhaust heat pipe section and an endothermic pipe section thermally connected to the vapor compression heat pump;
Operating the vapor compression heat pump so that the refrigerant condensing step is performed in the exhaust heat piping section and the refrigerant condensing step is performed in the heat absorbing piping section;
Including
The operation of the vapor compression heat pump is such that the temperature of water at the outlet side of the portion where heat is transferred to and from the vapor compression heat pump in the exhaust heat pipe section is 20 to 35 ° C. A water treatment method comprising controlling.