KR101782592B1 - method for controlling Heating and hot water supply system - Google Patents

Abstract

The present invention minimizes a heat loss generated by heat exchange for supplying heating and hot water in a mass energy demanding heat use facility in order to contribute to improvement of efficiency and significantly reduce a loss of exergy in order to significantly reduce proper energy and an emission amount of greenhouse gas.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a method for controlling heating and hot water supply systems,

The present invention relates to a control method of a heating and hot water supply system, and more particularly, to a control method of a heating and hot water supply system that increases the efficiency of a thermal energy consuming facility and minimizes the loss of exergy.

Generally, a large apartment or a large-scale building installs a common heating system not only for individual heating and individual hot water supply but also for the whole, and supplies hot water to each household through a common pipe network. In addition, the hot water is supplied to the household through the pipe network after the water is heated to a necessary temperature through the heat exchange between the hot water and the water supply.

This type of heating and hot water supply system corresponds to the use of collective energy heat, and it is possible to reduce the efficiency of the equipment compared to the individual supply method by using a heat source device having relatively high efficiency, And it is possible to reduce the total capacity of the equipment by applying the simultaneous usage rate and to collect firepower in one place and to cope with emergency such as fire easily.

In the prior art related to this type of heating and hot water supply, Korean Patent No. 10-1040693, entitled " Energy saving centralized heating and hot water supply system "has been proposed. This means that the hot water used for the production of hot water Reduces energy consumption by minimizing the amount of heat dissipated in the process of circulating the hot water to the main heat exchanger by circulating the hot water dispenser in the household or each floor, A main heat exchanger for supplying hot water, middle temperature water or steam from a heat production facility and producing hot water through heat exchange; A circulation pump for circulating the hot water to supply the hot water produced by the main heat exchanger to each household and each floor and recovering the hot water; A hot water heat exchanger installed in each household or each floor and producing hot water hot water through heat exchange between hot water supplied from the main heat exchanger and hot water for hot water supply; And a heater installed in each household or each floor for receiving hot water directly from the main heat exchanger or heating hot water used for producing hot water from the hot water heat exchanger, And a hot water distributor for circulating the hot water.

However, the prior art as well as other existing technologies are making progress in reducing the energy loss and improving the efficiency of the primary (collective energy heat source and transport facility), but the efficiency improvement of the secondary side There was still a problem that it was insufficient.

In addition, when a system is in an equilibrium state, theoretically the maximum available work is called an exergy. When the system changes, the energy is conserved (see Thermodynamics 1 Law ), Exergy is not preserved, and energy deals with quality aspects, while quantitative. In other words, it is a concept that considers entropy change in exergy energy (enthalpy) change. It can grasp qualitative change (loss, error, etc.) of energy which can not be grasped from the viewpoint of energy quantity, and can identify the point of loss. Heat and mass balance analysis on the input / output of the input heat can be used to identify the exergy status of each part after energy analysis and exergy analysis. Typical loss factors of such exergy include heat transfer, throttling, and mixing.

However, the conventional technologies for the hot water supply and heating supply system have limitations in increasing the efficiency of the heat utilization facility for the mass energy consumer, and the exergy loss is large as described above, which makes it difficult to save the proper energy.

In order to solve the problems of the prior art as described above, it is an object of the present invention to increase the efficiency of the heat utilization facility for collective energy consumers, minimize the loss of the exergy, and greatly contribute to the reduction of the appropriate energy.

Other objects of the present invention will become readily apparent from the following description of the embodiments.

In order to achieve the above object, according to one aspect of the present invention, there is provided a heating heat exchanger installed on a first branch line branched from a heat source supply line to which hot water for a heat source is supplied, A heating line for supplying water from the first demanding place to the heating heat exchanger so that the water supply becomes hot water for heating by heat exchange with hot water for the heat source to be supplied to the first demanding place; A hot water reheating heat exchanger installed on a second branch line branched from the heat source supply line after the first branch line and supplied with hot water for a heat source; A hot water supply line for supplying water to the hot water reheating heat exchanger from a second demanding place to supply hot water for hot water supply to the second demand place by heat exchange with hot water for hot water source; A hot water preheating heat exchanger to which the hot water for the heat source passing through the heat exchanger and the hot water reheating heat exchanger is supplied; And a preheating hot water supply line for supplying water to the hot water preheating heat exchanger so that water is supplied to the hot water reheating heat exchanger as preheated hot water by heat exchange with hot water for hot water source and supplied as hot water for hot water supply through the hot water supply line , A heating and hot water supply system is provided.

Wherein the heating line, the hot water supply line, and the preheated hot water supply line are each provided with a pump for supplying water, and the heating line bypasses the heating heat exchanger to return to the first demand place A bypass line provided between the first customer and the heating heat exchanger is installed in the heating line, and a differential pressure valve is installed in the bypass line, and the first branch line is connected to the first heat exchanger, The second branch line may be provided with a second temperature control valve at a rear end of the hot water reheating heat exchanger.

The hot water preheating heat exchanger may be installed in an integrated line in which the first and second branch lines are combined to receive the hot water for the heat source and discharged to the heat source recovery line.

According to another aspect of the present invention, there is provided a control method for a heating and hot water supply system according to an aspect of the present invention, which comprises the steps of: determining a heat quantity defined according to the outside air temperature; Calculating a supply-recovery temperature difference for controlling the temperature difference of the hot water for heating by repeating the increase and decrease of the temperature difference; The temperature of the hot water for hot water recovered through the heat exchanger according to the prescribed amount of heat is set by the control of the first temperature control valve installed in the first branch line and then flows into the heat exchanger as the target value Setting a flow rate of the water supply and controlling a discharge flow rate of the pump installed in the heating line so as to match the set flow rate; Calculating the actual amount of heat supplied from the supply temperature of the water supply supplied to the heating heat exchanger through the heating line, the recovery temperature and the flow rate of the hot water for heating supplied to the first customer from the heat exchanger; And repeatedly controlling the discharge flow rate of the pump installed in the heating line so that the difference between the actually supplied heat amount and the prescribed heat amount is within a set error range, and a control method of the heating and hot water supply system do.

In the control method of the heating and hot water supply system, it is possible to supply water from the first demander to the heat exchanger without bypassing the heat exchanger.

According to the control method of the heating and hot water supply system according to the present invention, it is possible to contribute to the efficiency increase by minimizing the heat loss generated in the heat exchange for heating and hot water supply in the heat using facility of the group energy consumer, Can greatly contribute to the reduction of appropriate energy and greenhouse gas emissions.

1 is a configuration diagram showing a heating and hot water supply system according to an embodiment of the present invention.
2 is a flowchart illustrating a control method of a heating and hot water supply system according to an embodiment of the present invention.
3 is a block diagram showing a main part of a heating and hot water supply system according to an embodiment of the present invention.
FIGS. 4 and 5 are graphs showing the effect of the bypass on the efficiency of heat using facilities for the heat exchanger, FIG. 4 shows a conventional bypass, and FIG. 5 shows a bypass after the bypass.
FIGS. 6 to 9 are graphs showing intrinsic characteristics of exergy efficiency according to changes in the supply-recovery temperature difference and the outside temperature of each of the heat utilization facilities.
10 to 13 are graphs showing results calculated by applying the sawtooth temperature difference control method of the present invention to each of the heat utilization facilities.
14 is a graph showing an example of a conventional temperature difference control method.
15 to 18 are graphs showing the intrinsic characteristics of exergy efficiency according to the supply-recovery temperature difference and the outside air temperature change of the four heat utilization facilities.
19 to 22 are graphs showing the results to be calculated by applying the optimum tooth form temperature difference control method of the present invention to four thermal utilization facilities.

The present invention is capable of various modifications and various embodiments, and specific embodiments are illustrated and described in detail in the drawings. It is to be understood, however, that the invention is not to be limited to the specific embodiments, but is to be understood to cover all modifications, equivalents, and alternatives falling within the spirit and scope of the invention, And the scope of the present invention is not limited to the following examples.

Hereinafter, embodiments according to the present invention will be described in detail with reference to the accompanying drawings, wherein like or corresponding elements are denoted by the same reference numerals, and redundant explanations thereof will be omitted.

1 is a configuration diagram showing a heating and hot water supply system according to an embodiment of the present invention.

Referring to FIG. 1, a heating and hot water supply system 100 according to an embodiment of the present invention includes a heating heat exchanger 120, a heating line 130, a hot water reheating heat exchanger 150, a hot water supply line 160, A preheat heat exchanger 170 and a preheated hot water line 180. Meanwhile, in the present invention, the first and second demanders are heat-utilizing facilities, and can represent a household in the case of an apartment, and a building can represent a specific area in each floor or a floor. In FIG. 1, MP1 denotes a second heat recovery, MP2 denotes an inlet of the hot water preheating heat exchanger 170, and MP3 denotes a place where hot water supply water and hot water return water are combined.

The heat exchanger 120 is installed on the first branch line 110 branched from the heat source supply line 10 for providing a path for supplying the hot water for the heat source to the collective energy heat utilization facility, It is supplied. Here, a pressure reducing valve 11 may be installed in the heat source supply line 10.

The heating line 130 supplies water to the heating heat exchanger 120 from the first customer as a secondary side so that the water is heated by the heat exchange with the hot water for the heat source to be supplied to the first consumer.

The hot water reheating heat exchanger 150 is installed on the second branch line 140 branched from the heat source supply line 10 after the first branch line 110 and receives the hot water for the heat source as a primary side. That is, the second branch line 140 branches from the rear end of the portion where the first branch line 110 branches to the heat source supply line 10 to supply the hot water for the heat source to the hot water reheat heat exchanger 150

The hot water supply line 160 supplies water to the hot water reheating heat exchanger 150 as a secondary water from the second demand point so that the hot water is supplied to the second demand point by heat exchange with hot water for hot water.

The hot water preheating heat exchanger 170 is supplied with hot water for the heat source which has passed through the heat exchanger 120 and the hot water reheating heat exchanger 150. The hot water preheating heat exchanger 170 may be installed in an integrated line 190 that allows the first and second branch lines 110 and 140 to be combined to be supplied with hot water for the heat source and discharged to the heat source recovery line 20. The integrated line 190 may be connected to the front end of the hot water reheat heat exchanger 150 in the hot water supply line 160. On the other hand, the heat source recovery line 20 may be provided with a flow meter 21.

The preheating hot water supply line 180 supplies water to the hot water preheating heat exchanger 170 so that the water is supplied to the hot water reheating heat exchanger 150 by the heat exchange with the hot water for the heat source, And supplied as hot water for hot water supply. That is, the preheating hot water supply line 180 supplies the preheated hot water generated by the heat exchange between the feed water and the hot water for the heat source in the hot water preheating heat exchanger 170 to the hot water reheating heat exchanger 150 as supplementary water to be used as hot water for hot water supply do.

The heating line 130, the hot water supply line 160 and the preheated hot water supply line 180 may be provided with pumps 131, 161 and 181 for supplying water, respectively. In the heating line 130, The bypass line 132 installed between the first customer and the heating heat exchanger 120 may be installed in the heating line 130 so that the bypass line 132 can be bypassed and recovered to the first customer. A differential pressure valve 133 may be provided. The first branch line 110 may be provided with a first temperature control valve 111 at the rear end of the heating heat exchanger 120 and the second branch line 140 may be provided at a rear end of the hot water reheat heat exchanger 150 2 temperature control valve 141 may be provided.

FIG. 2 is a flowchart illustrating a method of controlling a heating and hot water supply system according to an embodiment of the present invention, and FIG. 3 is a block diagram illustrating a main part of a heating and hot water supply system according to an embodiment of the present invention. The control method of the heating and hot water supply system according to an embodiment of the present invention is a method of controlling the heating and hot water supply system 100 according to the present invention. Time). The control unit receives the sensing or measurement signal from the sensor or the measuring device necessary for the control according to the present invention, and performs control on the control target accordingly.

3, T _1s , T _2s, and m ₁ represent the supply temperature, the recovery temperature, and the flow rate of the hot water for the primary heat source supplied from the district heating corporation, and T _2s , T _2r, and m ₂ represent the supply temperature, Temperature, and flow rate of the hot water for heating the secondary side circulated to the household. The first and second temperature sensors 135 and 136 measure and transmit the recovery temperature T _2r and the supply temperature T _{2s of the} secondary side and the first temperature control valve 111 is connected to the heating heat exchanger 110 at 1 And controls the temperature T _{2s on the} secondary side. The flow rate of the pump 131 is controlled by the control of the inverter 134. The flow rate of the pump 131 is measured using a flowmeter 137 provided at the rear end of the pump 131 and is transmitted to a control unit do.

Referring to FIGS. 2 and 3, a method for controlling a heating and hot water supply system according to an embodiment of the present invention includes: obtaining a prescribed amount of heat according to outdoor air temperature; The temperature difference of the hot water for heating recovered to the customer is repeatedly increased and decreased to calculate the supply-recovery temperature difference for controlling in the form of sawtooth (S11), that is, if the outside temperature (T _? ) Is given as the first step of the control procedure, _{Determine the} specified calorie (Q _spec ) and calculate the feed-temperature difference (DT) in the form of a saw tooth in accordance with the characteristics of the thermal facility.

Optimum supply proposed in the present invention recovered the temperature difference control method, the supply heat quantity (Q _spec) and supplies a saw tooth form defined for heating with respect to Fig given outside temperature (T _∞) - Calculate the number of times the temperature difference (DT) preferentially . The relationship between the supplied heat quantity and the supplied heat quantity at a given outside temperature condition can be expressed by the following equations (1) and (2).

The control method of the heating and hot water supply system according to an embodiment of the present invention is performed by using Equations (1) and (2) and (3).

The temperature of the hot water for the heat source, which is recovered through the heat exchanger 120 according to the prescribed amount of heat, is set at a first temperature The flow rate of the feed water flowing into the heating heat exchanger 120 is set as the target value after the control by the control valve 111 and the discharge flow rate of the pump 131 installed in the heating line 130 is adjusted so as to match the set flow rate (S12). That is, the primary-side recovery temperature T _1r is set using the first temperature regulating valve 111 based on the obtained prescribed amount of heat Q _spec , the secondary-side flow rate m ₂ is set as the target value, The discharge flow rate of the pump 131 is adjusted by using the inverter 134 of the pump 131 in accordance with the flow rate.

Then, the amount of heat actually supplied from the supply temperature of the feed water supplied to the heating heat exchanger 120 through the heating line 130, the recovery temperature of the hot water for heating supplied to the first customer from the heat exchanger 120 and the flow rate is calculated (S13). That is, by using the first and second temperatures 135 and 136 installed in the secondary piping system and the supply temperature T _2s , the recovery temperature T _2r , and the flow rate m _{2 of the} secondary side water transferred from the flow meter 137 , And the actually supplied heat quantity Q 'is obtained.

The actual flow rate of the pump 131 is controlled so as to control the flow rate of the pump 131 installed in the heating line 130 so that the difference between the actual amount of heat supplied and the prescribed amount of heat is within a predetermined error range. That is, by comparing the obtained heat quantity Q 'with the prescribed heat quantity _Qspec , the inverter 134 is used to control the flow rate of the pump 131 until the difference is within the allowable error range? Lt; / RTI >

On the other hand, during the above-described steps S11 to S14, it is possible to supply the water supply from the first demanding place to the heat exchanger 120 without bypassing the heat exchanger 120. [

The operation of the heating and hot water supply system and its control method according to the present invention will now be described.

Through the exergy analysis of the thermal facility, the efficiency of the thermal facility is greatly affected by the operating conditions of the heat exchangers (120, 150, 170) in the facility. The hot water reheating heat exchanger 150 and the hot water preheating heat exchanger 170 in the heat exchangers 120, 150 and 170 are different from each other in the hot water supply demand (hot water consumption) in the field and are very irregular. And it is practically difficult to optimize it. Therefore, it is preferable to assume that the hot water preheating heat exchanger 170 is operated under fixed operating conditions except for the efficiency improvement target. Accordingly, it is necessary to improve the efficiency of the heat utilization facility mainly with respect to the heat exchanger 120. At this time, factors that greatly affect the performance of the heat exchanger 120 and the efficiency of the entire facility are the heat exchange (DT) and the bypass ratio.

Mixing the supply water of the heat exchanger 120 with the hot water for heating of the first customer to lower the performance of the heat exchanger 120 and the efficiency of the first customer. As shown in FIGS. 4 and 5, exergy analysis is performed by fixing all other operating conditions in the same manner and bypassing the bypass heat exchanger 120 (by-pass ratio = 0%) as in the present invention, The results were compared with the results of the conventional bypass operation. For an equal comparison of each facility, the outside temperature was assumed to be 0 ^° C. If the bypass is shut off, all of the thermal facilities are shown to have improved efficiency from less than 2% to as much as 6%, which improves the efficiency of the thermal facility with bypass blocking alone.

The heating heat exchanger 120 receives heat from the heat source water for the primary heat source and heats the water circulating through the heating heat exchanger 120 and supplies the heated water to the first customer. At this time, the heating heat exchanger 120 performs heat exchange (Or the amount of heat supplied to the household) Q is given by Equation 3 below.

Here, m is the secondary circulation flow, C _p is specific heat of water, T _s is the temperature of the heating water, T _r is supplied to the first demand in nanbangyeol exchanger means the temperature of the water that is recovered by nanbangyeol exchanger from the first demand . Temperature difference between the water supply and heating of hot water nanbangyeol exchanger 120, i.e., supply-recovery temperature difference (DT) is defined as (T _s -T _r), the supply of nanbangyeol exchanger 120 according to the outside air temperature (T _∞) - It is possible to maximize the efficiency of the heat exchanger and the efficiency of the heat utilization facility by changing the recovery temperature difference DT.

In order to grasp the optimal heat exchanger operating condition (or supply-recovery temperature difference) of the heat exchanger 120, it is necessary to grasp the inherent characteristics of the exergy efficiency according to the supply-recovery temperature difference and the outside temperature of the heat utilization facility, For this, the exergy efficiency of the thermal facility was calculated by varying the supply - recovery temperature difference (DT) for a given outdoor temperature, based on the operating data for the thermal facilities. In this calculation, it was assumed that the heat quantity Q supplied to the heat exchanger 120 was constant. To this end, the operating conditions were fixed and the supply-recovery temperature difference DT was changed through the increase of the supply temperature T _s , And furthermore, the flow rate (m) was adjusted in accordance with the change of the supply-withdrawal temperature difference (DT) in order to supply a certain amount of heat (Q).

6 to 9 show the inherent characteristics of the exergy efficiency according to the supply-recovery temperature difference and the outside temperature change of the four heat utilization facilities. It can be seen that the exergy efficiency of the thermal facility is increased by increasing the supply-recovery temperature difference from 15 ^° C to 20 ^° C for the ambient temperature, which is similar to that for all thermal facilities .

According to these results, as shown by the dotted line in the example of FIG. 7, it is possible to derive the optimal supply-recovery temperature difference operation mode according to the change of the outside air temperature. In other words, if the entire section of the outside temperature is divided into several limited sections and the supply-recovery temperature difference is increased along the iso-efficiency line in accordance with the increase of the outside temperature within each section, By performing a saw-tooth shaped temperature difference control that repeatedly performs the increase-decrease and the increase-decrease of the supply-recovered temperature difference according to the outside temperature, Thereby improving the efficiency.

Table 1 below shows an example of the algorithm for controlling the feed-back temperature difference of the sawtooth type mentioned above. The outer temperature range of -15 to +15 ^° C is divided into 10 intervals, and 15 to 20 ^o The temperature difference control method within the range of C is expressed by the formula.

Outside atmospheric
온도
(X, ^o C) Supply-return temperature difference
(Y, ^o C) Exergy efficiency
improvement (Dhex) -15 <x <-12 Y = 15.0 + 1.50 (X + 15) +2.1 to +4.8% -12 <x <-8 Y = 15.0 + 1.25 (X + 12) + 2.3 to + 5.8% -8 < x < Y = 15.0 + 1.25 (X + 8) +2.7 to +5.9% -4 < x < -1 Y = 15.2 + 1.60 (X + 4) +2.7 to +5.6% -1 < x < 3 Y = 15.6 + 1.10 (X + 1) +3.5 ~ +6.1% 3 < x < 5 Y = 16.2 + 1.90 (X-3) +3.0 to +6.4% 5 < x < 8 Y = 16.2 + 1.27 (X-5) +3.4 to +7.5% 8 < x < 11 Y = 16.7 + 1.10 (X-8) +4.1 to +7.8% 11 < x < 13 Y = 17.0 + 1.50 (X-11) +3.9 ~ +7.4% 13 < x < 15 Y = 17.0 + 1.40 (X-13) +3.9 ~ +7.2%

FIGS. 10 to 13 show results calculated by applying the above-mentioned optimum sawtooth temperature difference control method to four heat utilization facilities. Here, the calculation result of the temperature difference control method of the sawtooth type according to the present invention is compared with the calculation result of the constant temperature difference control method.

From the comparison results of the four heat utilization facilities, the sawtooth type temperature difference control method of the present invention shows a remarkable improvement in exergy efficiency over the entire outside temperature temperature range compared to the constant temperature difference control method. As shown in <Table 1>, the efficiency improvement effect is improved by at least 2% and up to 8% in each section, compared to a certain temperature difference.

For a more practical field application of the optimal supply-recovery temperature difference control method of the heat exchanger 120 proposed in the present invention, the calorie supplied according to the variation of the outside air temperature (or seasonality) was varied and the result was calculated.

In the field of actual heat use facilities, the heat quantity to be supplied to the household is changed linearly according to the outside temperature (season), and the supply temperature of the heat exchanger is controlled linearly to control the heat quantity. As shown in FIG. 14, the supply temperature of the heating heat exchanger is set to 50 ^° C. in the condition that the outside air temperature is 10 ^° C. (cold weather), and the supply temperature is decreased according to the increase of the outside temperature , The temperature is set at 42 ^o C, which is close to the recovery temperature, under the condition that the heating is not required and the outside temperature is +10 ^o C (Lunar New Year). As can be seen from Equation (3), the heating heat Q supplied from the heat exchanger 120 to the household decreases linearly with the increase of the outside temperature according to the change of the supply temperature. This change in the supply temperature also means that the supply-recovery temperature difference control method used in the field is linear.

In the present invention, the exergy efficiency of a heat utilization facility is calculated by changing the supply-recovery temperature difference (DT) with respect to a given outside temperature. In this calculation, the amount of heat Q supplied to the heat exchanger 120 is limited to the value of the specified amount of heat for a given outside temperature, and it is assumed that the amount of supplied heat varies with the change in outside temperature. Therefore, in this calculation, in the formula (3), the recovery temperature (T _r ) is fixed to the operating condition and the supply-recovery temperature difference DT is changed by increasing the supply temperature (T _s ) In order to supply the amount of heat Q to be varied, the flow rate m was also adjusted according to the change in the supply-return temperature difference DT.

15 to 18 show the intrinsic characteristics of the exergy efficiency according to the supply-recovery temperature difference and the outside temperature change of the four heat utilization facilities. It can be seen that increasing the supply-recovery temperature difference from 15 ^° C to 20 ^° C for a given outdoor temperature increases the exergy efficiency of the thermal facility, Similar. 15 to 18, in which the supply of heat is changed, the exergy efficiency is relatively changed according to the changes in the outside air temperature, as compared with Figs. 10 to 13, which are the results of the case where the supply of heat is constant. And the efficiency of the heat exchanger is rapidly lowered as the temperature of the heat exchanger is changed.

From the results shown in FIGS. 15 to 18, even when the amount of heat supplied varies according to the ambient condition, it can be considered that the optimal supply-recovery temperature difference operation method according to the change in the ambient temperature described above can be applied. That is, the efficiency of the heat-using facility can be improved by performing a saw-tooth shaped temperature difference control which repeatedly performs the increase-decrease and the increase-decrease of the supply-recover temperature difference according to the outside temperature.

Figs. 19 to 22 show the results to be calculated by applying the above-mentioned optimum tooth shape temperature difference control method to four heat utilization facilities. Here, the calculation result of the optimum temperature difference control method is compared with the calculation result of the conventional linear temperature difference control method.

From the comparison results of the four heat utilization facilities, the sawtooth temperature difference control method of the present invention shows a remarkable exergy efficiency improvement of 2 to 7% over the entire outside temperature temperature range compared to the conventional linear temperature difference control method .

Table 2 below shows the efficiency-related data of the thermal facility according to the bypass ratio. Table 3 below shows the case where the hot water preheat heat exchanger 170 is not applied as in the present invention, , And Table 4 below shows the exergy efficiency of these thermal facilities. Here, HX1 represents the heat exchanger 120, HX2 represents the hot water reheating heat exchanger 150, and HX represents the hot water preheating heat exchanger 170. [

According to Tables 2 to 4 above, the A apartment is operated at a high heat exchanger temperature difference and a low bypass ratio as shown in the present invention, as compared to the B apartment, resulting in high exergy efficiency. It can be seen that the C apartment maintains a higher exergy efficiency than the D apartment despite the low temperature difference of the heat exchanger 120 due to the application of the hot water preheating heat exchanger 170 and the high efficiency operation as in the present invention have. Particularly, in the case of the D apartment where the hot water preheating heat exchanger 170 is not applied, it can be seen that the exergy efficiency is deteriorated due to a relatively large amount of exergy destruction and loss.

According to the heating and hot water supply system and the control method of the present invention, it is possible to contribute to the efficiency increase by minimizing the heat loss generated in the heat exchange for the heating and hot water supply in the heat utilization facility for the group energy user, Significant reductions in losses can significantly contribute to the reduction of appropriate energy and greenhouse gas emissions.

Although the present invention has been described with reference to the accompanying drawings, it is to be understood that various changes and modifications may be made without departing from the spirit and scope of the present invention. Therefore, the scope of the present invention should not be limited to the described embodiments, but should be determined by the scope of the appended claims and equivalents thereof.

10: heat source supply line 11: pressure reducing valve
20: heat source recovery line 21: flow meter
110: first branch line 111: first temperature control valve
120: heat exchanger 130: heating line
131: Pump 132: Bypass line
133: Differential pressure valve 134: Inverter
135: first temperature sensor 136: second temperature sensor
137: Flow meter 140: Second branch line
141: second temperature control valve 150: hot water reheat heat exchanger
160: Hot water supply line 161: Pump
170: hot water preheating heat exchanger 180: preheated hot water supply line
181: Pump 190: Integrated line

Claims (5)

delete delete delete A heating heat exchanger installed on a first branch line branched from a heat source supply line supplied with hot water for a heat source and supplied with hot water for a heat source; A heating line for heating the heating water to be supplied to the first customer and heating the heating water to be supplied to the first demanding place by bypassing the heating heat exchanger, A hot water supply heat exchanger installed on a second branch line branched from the heat source supply line after the first branch line and supplied with hot water for a heat source; A hot water supply line for supplying water to the hot water reheating heat exchanger from a second customer and supplying the water to hot water for hot water by heat exchange with the hot water for the heat source to be supplied to the second customer; A hot water preheating heat exchanger to which the hot water for the heat source passing through the heat exchanger and the hot water reheating heat exchanger is supplied; And a preheating hot water supply line for supplying water to the hot water preheating heat exchanger so that water is supplied to the hot water reheating heat exchanger as hot water by heat exchange with hot water for hot water source and supplied as hot water for hot water supply through the hot water supply line, A method for controlling a hot water supply system,
Calculating a supply-recovery temperature difference for controlling the temperature of the heating water to be supplied to the heating heat exchanger and the heating water for heating to be returned to the first customer, Wow;
The temperature of the hot water for hot water recovered through the heat exchanger according to the prescribed amount of heat is set by the control of the first temperature control valve installed in the first branch line and then flows into the heat exchanger as the target value Controlling the discharge flow rate of the pump installed in the heating line so as to match the flow rate set by setting the flow rate of the water supply;
Calculating the actual amount of heat supplied from the supply temperature of the water supply supplied to the heating heat exchanger through the heating line, the recovery temperature and the flow rate of the hot water for heating supplied to the first customer from the heat exchanger; And
And repeatedly controlling the discharge flow rate of the pump so that the difference between the actually supplied heat amount and the prescribed heat amount is within a set error range. The method of claim 4,
And the water supply from the first demanding place is supplied to the heating heat exchanger without bypassing the heating heat exchanger through the bypass line.

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