KR101984241B1 - Method for calculation of heating value of brine-refrigerant type heat pump system using geothermal heat energy - Google Patents

Abstract

According to the present invention, a brine-refrigerant type heat pump system using geothermal heat can calculate produced heating values of a heating source using brine, and calculate consumed heating values of a demand from the produced heating values of the heating source, and thus costs can be reduced as high-priced refrigerant flowmeter is unnecessary to calculate heating values of the demand using a refrigerant. Moreover, on/off points of a brine pump and the heat pump are differently controlled, and the produced heating values of the heating source is calculated to be estimated while the brine pump is turned on. Therefore, heating values can be accurately calculated.

Description

[0001] The present invention relates to a brine-refrigerant type heat pump system using geothermal heat,

The present invention relates to a method of calculating a heat quantity of a brine-refrigerant heat pump system using geothermal heat, and more particularly to a brine-refrigerant heat pump system using a brine as a medium on a heat source side and a refrigerant as a medium on a demand side The present invention relates to a heat calculation method of a brine-refrigerant type heat pump system that utilizes geothermal heat that can calculate the heat consumption on the demand side by calculating the heat generated by the heat source using the brine.

Generally, a heat pump is an air heat source system that obtains or discharges heat in the atmosphere, a hydrothermal source system that discharges heat through a cooling tower, and a geothermal system that obtains heat from the ground or discharges heat to the ground.

Since the ground temperature can be maintained almost constant when the depth of the ground is above a certain depth, the geothermal circulation system has an advantage of energy efficiency higher than the air heat source system. In the case of summer cooling, a large amount of electric power is consumed in order to discharge the cooling heat because the air temperature is very high at 30 ° C or more in the air. However, in the geothermal circulation system, the temperature of the ground is 10 to 20 ° C It is much lower than the temperature, so it is easy to discharge the cooling heat, so the efficiency is high. In case of winter heating, it is difficult to supply the heat required for heating because the air temperature is very low in the air. However, since the temperature of the ground is 10 to 20 ℃ higher than the atmospheric temperature, Can be supplied to the heat pump.

In the case of a heat pump using geothermal heat, it is necessary to measure the geothermal energy used for cooling and heating more accurately in order to use geothermal heat more efficiently.

On the other hand, in the case of a brine-brine type heat pump using a medium on the heat source side such as an underground source and a demand side medium using a heat source such as a building as a brine, the flow rate of the brine is relatively low Therefore, it is easy to measure the demand side heat quantity. The brine-brine method is also generally referred to as a water-water method. The brine refers to a mixture of water and ethanol.

However, in the case of a brine-refrigerant type heat pump using a brine as the medium on the heat source side and a refrigerant as the medium on the demand side, most of the flow meters for measuring the flow rate of the refrigerant are expensive and the flowmeters vary depending on the type of the refrigerant. Therefore, it is very difficult and costly to directly calculate or measure the demand side heat quantity. The brine-refrigerant system is also commonly referred to as a water-air system.

Korean Patent No. 10-0496895

It is an object of the present invention to provide a brine-refrigerant type heat pump which uses refrigerant as a demand-side medium, calorific calculation of a brine-refrigerant type heat pump system that utilizes geothermal heat that can more easily and accurately calculate demanded heat quantity on demand side ≪ / RTI >

A method for calculating a heat amount of a brine-refrigerant heat pump system using geothermal heat according to the present invention is a method for calculating a heat amount of a brine-refrigerant heat pump system using a geothermal heat source, comprising a geothermal heat exchanger providing a heat source, a heat pump installed in a machine room, a demand side heat exchanger provided with the heat source, A brine circulating flow path connecting the heat pump and circulating the brine, a refrigerant circulating flow path connecting the heat pump and the demand side heat exchanger to circulate the refrigerant, a brine installed in the brine circulating flow path inside the machine room to pump the brine A pump, a brine flowmeter installed in the brine circulation channel inside the machine room for measuring the flow rate of the brine, a brine flowmeter installed in the brine circulation channel inside the machine room and measuring the inflow temperature of the brine before entering the underground heat exchanger 1 < / RTI > temperature sensor, And a second temperature sensor installed in the oil-oil path and measuring the discharge temperature of the brine before the flow-out from the underground heat exchanger and flowing into the heat pump, the brine-refrigerant heat pump system comprising: Turning on the heat pump after a first set time has elapsed; Calculating and accumulating the heat quantity on the heat source side in real time using the inflow temperature of the brine, the discharge temperature of the brine, the flow rate of the brine, and the specific heat of the brine from the time when the brine pump is turned on; Turning off the brine pump after a second set time after turning off the heat pump; When the brine pump is turned off, calculation of the heat-source-side heat quantity and stopping the integration are stopped.

A method of calculating a calorie of a brine-refrigerant heat pump system using geothermal heat according to another aspect of the present invention includes calculating a calorific value of a brine-refrigerant type heat pump system using geothermal heat by using a geothermal heat exchanger providing a heat source, a heat pump installed in a machine room, A brine circulating flow path connecting the heat exchanger and the heat pump to circulate the brine, a refrigerant circulating flow path connecting the heat pump and the demand side heat exchanger to circulate the refrigerant, A brine flow meter installed in the brine circulation flow path inside the machine room for measuring the flow rate of the brine, a brine flow meter installed in the brine circulation flow path inside the machine room and having an inflow temperature of the brine before being introduced into the underground heat exchanger, A first temperature sensor for measuring the temperature, A brine-refrigerant heat pump system using a geothermal heat source, the brine pump comprising: a brine heat exchanger installed in a brine circulation channel and measuring a discharge temperature of the brine before flowing into the heat pump; Turning on the heat pump after a first predetermined time has passed; Calculating and accumulating the heat quantity on the heat source side in real time using the inflow temperature of the brine, the discharge temperature of the brine, the flow rate of the brine, and the specific heat of the brine from the time when the brine pump is turned on; And calculating and integrating the demand side consumed heat quantity using the heat source side heat quantity and the heat pump performance coefficient (COP).

In the brine-refrigerant heat pump system using geothermal heat according to the present invention, the calorific value on the heat source side using the brine is calculated, and the demand side calorific value using the heat source side calorific value is calculated. There is no need to use an expensive refrigerant flow meter or the like.

Further, by controlling the on / off points of the brine pump and the heat pump differently and calculating the heat-source-side heat-generation amount while the brine pump is on, the heat quantity can be calculated more accurately.

1 is a view showing a configuration of a brine-refrigerant type heat pump system using geothermal heat according to an embodiment of the present invention.
FIG. 2 is a graph showing changes in the inflow temperature and the discharge temperature of the brine during the summer cooling operation of the brine-refrigerant heat pump system using geothermal heat according to the embodiment of the present invention.
FIG. 3 is a graph showing changes in the inflow temperature and the discharge temperature of the brine during the winter heating operation of the brine-refrigerant type heat pump system using geothermal heat according to the embodiment of the present invention.

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

1 is a view showing a configuration of a brine-refrigerant type heat pump system using geothermal heat according to an embodiment of the present invention.

1, a brine-refrigerant type heat pump system using geothermal heat according to an embodiment of the present invention includes an underground heat exchanger 10, a heat pump 20, a demand side heat exchanger 30, A refrigerant circulation channel 50, a brine pump 60, a brine flow meter 70, a first temperature sensor 81, a second temperature sensor 82 and a control unit (not shown).

The underground heat exchanger (10) is a heat exchanger embedded in the ground to provide a heat source in the ground. The underground heat exchanger (10) is connected by the heat pump (20) and the brine circulating flow passage (40).

The heat pump (20) is installed in the machine room (21). The heat pump (20) receives a heat source from the underground heat exchanger (10) and provides a heat source to the demand side heat exchanger (30). One side of the heat pump 20 is connected to the brine circulation channel 40 and the other side is connected to the refrigerant circulation channel 50. Therefore, the heat pump 20 is a brine-refrigerant type heat pump. The brine-refrigerant system is also commonly referred to as a water-air system. The brine includes a fluid to which ethanol or the like is added based on water.

The heat pump 20 includes a compressor (not shown), a first heat exchanger (not shown), a second heat exchanger (not shown) and an expansion device (not shown).

The demand side heat exchanger (30) is an indoor unit installed in an interior of a building (31) different from the machine room. The demand side heat exchanger 30 serves as an evaporator during a summer cooling operation and a condenser during a winter heating operation.

The brine circulating flow path 40 connects the underground heat exchanger 10 and the heat pump 20 to circulate the brine. The brine circulating flow path 40 includes a brine inflow path 41 for guiding the brine coming from the heat pump 20 into the underground heat exchanger 10 and a brine inflow path 41 extending from the underground heat exchanger 10 And a brine discharge passage (42) for guiding the discharge to the heat pump (20).

The brine pump 60 is installed in the brine inflow passage 41 and pumps the brine to flow into the underground heat exchanger 10.

The brine flow meter 70 is installed in the brine discharge flow passage 42 and measures the flow rate of the brine discharged from the underground heat exchanger 10.

Both the brine pump 60 and the brine flow meter 70 are installed inside the machine room 21.

The first temperature sensor (81) is installed in the brine inflow passage (41). The first temperature sensor 81 measures the inflow temperature of the brine before it flows into the underground heat exchanger 10 from the heat pump 20.

The second temperature sensor (82) is installed in the brine discharge passage (42). The second temperature sensor 82 measures the discharge temperature of the brine before being supplied to the underground heat exchanger 10 and discharged to the heat pump 20.

The first and second temperature sensors 81 and 82 are all installed inside the machine room 21.

The controller (not shown) controls the operation of the brine pump 60 and the heat pump 20.

In the embodiment of the present invention, the brine pump 60 for measuring the flow rate of the brine, the inflow temperature and the discharge temperature of the brine flow meter 70, the brine flow meter 70, The first temperature sensor 81, and the second temperature sensor 82 are provided.

That is, since it is not necessary to measure the flow rate of the refrigerant circulating on the demand side or the temperature of the refrigerant, it is not necessary to provide a refrigerant flow meter having a higher price than the brine flow meter.

The operation of the brine-refrigerant heat pump system using geothermal according to the present invention will be described below.

First, the cooling operation in summer will be described.

The temperature Tg of the underground is lower than the temperature Tm of the machine room 21 during the summer and lower than the temperature of the brine in and out of the heat pump 20 when the heat pump 20 is driven, The cool air in the ground can be supplied to the heat pump 20.

When the cooling operation mode is selected by the user's operation, the control unit (not shown) turns on the brine pump 60.

The heat pump 20 is not turned on when the brine pump 60 is turned on.

The inflow temperature Tin of the brine is measured by the first temperature sensor 81 from the time when the brine pump 60 is turned on and the discharge temperature Tout of the brine is measured by the second temperature sensor 82 .

Referring to FIG. 2, when the brine pump 60 is driven, the temperature of the brine on the brine circulation channel 40 can be known.

The inlet temperature Tin of the brine and the outlet temperature Tout of the brine are substantially equal to or the same as the temperature Tm of the machine room 21 before the brine pump 60 is driven.

When the brine pump 60 is turned on, the discharge temperature Tout of the brine that has passed through the underground heat exchanger 10 gradually decreases to a temperature substantially equal to or lower than the temperature Tg of the ground.

Further, the brine inflow temperature (Tin) gradually decreases to a temperature substantially equal to or lower than the temperature (Tg) of the ground.

At this time, the discharge temperature Tout of the brine from the underground heat exchanger 10 is lower than the brine inflow temperature Tin because the temperature Tg of the underground is the lowest.

 That is, it can be seen that the heat pump 20 is off, but there is a temperature difference between the brine inflow temperature Tin and the discharge temperature Tout.

Thereafter, when the brine pump 60 is turned on, the heat pump 20 is turned on after a preset first set time t1.

The first set time? T1 is about 2 minutes to 3 minutes, for example.

The first set time? T1 may be set according to the inflow temperature Tin of the brine. That is, the brine inflow temperature Tin may be set in consideration of the fact that the brine inflow temperature Tin is substantially equal to or lower than the ground temperature Tg.

The first set time t1 may be set to a time until the difference between the inflow temperature Tin of the brine and the discharge temperature Tout of the brine becomes equal to or less than a preset first temperature difference . That is, while only the brine pump 60 is driven, a temperature difference between the brine inflow temperature Tin and the brine discharge temperature Tout occurs, and the temperature difference is less than the first temperature difference, The heat pump 20 can be driven.

When the heat pump 20 is turned on, a brine introduced into the heat pump 20 through the brine discharge passage 42 provides cool air to the heat pump 20, absorbs heat, Flows into the underground heat exchanger (10) through the flow path (41).

Referring to FIG. 2, the inflow temperature Tin of the brine measured by the first temperature sensor 81 rises to a predetermined temperature while the heat pump 20 is driven.

Further, the discharge temperature Tout of the brine measured by the second temperature sensor 82 also rises to a predetermined temperature.

The difference between the inlet temperature Tin of the brine and the outlet temperature Tout of the brine is a difference in the amount of heat that provides the geothermal heat to the heat pump 20.

The heat source provided to the heat pump 20 is transferred to the refrigerant circulating in the refrigerant circulation channel 50 and supplied to the demand side heat exchanger 30. [

The refrigerant is cooled by the heat pump 20 and then supplied to the demand side heat exchanger 30 via the refrigerant circulation flow path 50. The heat is absorbed by the demand side heat exchanger 30, And circulates to the heat pump 20.

Thereafter, when the stop of the cooling operation mode is selected by the user's operation, the control unit (not shown) turns off the heat pump 20. At this time, the brine pump 60 is in the driving state.

2, when the heat pump 20 is turned off, it can be seen that the inlet temperature Tin and the discharge temperature Tout of the brine are substantially equal to or lower than the temperature Tg of the ground .

The brine pump 60 is turned off after a predetermined second set time? T2 after the heat pump 20 is turned off.

The control unit (not shown) does not turn off the heat pump 20 and the brine pump 60 at the same time. The brine pump 60 is further operated during the second set time period? T2 to take out the brine in the brine circulation channel 40 to the heat pump 20 side even after the heat pump 20 is turned off .

The second set time? T2 is set longer than the first set time? T1. The second set time may be set to a time until a difference between the inflow temperature Tin of the brine and the discharge temperature becomes equal to or less than a preset second set temperature difference.

Even when the heat pump 20 is turned off, there is a temperature difference between the inflow temperature Tin and the discharge temperature Tout of the brine until the brine pump 60 is turned off. Therefore, It is preferable to integrate until the brine pump 60 is turned off.

Meanwhile, a method of calculating the heat quantity of the brine-refrigerant type heat pump system during the summer cooling operation is as follows.

The control unit (not shown) calculates and integrates the heat-source-side heat quantity Q_brine in real time from when the brine pump 60 is turned on until the brine pump 60 is turned off.

There is a temperature difference between the inflow temperature Tin and the discharge temperature Tout of the brine before the heat pump 20 is turned on after the brine pump 60 is turned on and the heat pump 20 is turned off Thereafter, even before the brine pump 60 is turned off, there is a temperature difference between the brine inflow temperature Tin and the discharge temperature Tout.

Therefore, the time for calculating the heat-source-side heat quantity Q_brine is set as the time when the brine pump 60 is operated.

The heat-source-side heat quantity Q_brine is calculated and integrated in real time using the inflow temperature of the brine, the discharge temperature of the brine, the flow rate of the brine, and the specific heat of the brine.

Equation (1) is an equation for measuring the heat quantity Q_brine on the heat source side during the cooling operation.

[Equation 1]

Here, ΔT is a difference value between the brine inflow temperature Tin measured by the first and second temperature sensors 81 and 82 and the brine discharge temperature Tout. The flow rate m of the brine is a value measured by the brine flow meter 70, and the specific heat C of the brine is a known value.

Using the equation (1), the heat source-side heat quantity Q_brine can be calculated and integrated in real time while the brine pump 60 is driven. In this embodiment, the integration is performed in units of seconds, for example.

On the other hand, a method of obtaining the demand side consumed heat quantity Q_load from the heat source side heat quantity Q_brine is as follows.

Equation (2) represents the relationship between the heat-source-side heat quantity Q_brine and the demand-side heat quantity Q_load according to the first law of thermodynamics.

&Quot; (2) "

Equation (3) represents the coefficient of performance (COPc) during the cooling operation of the heat pump.

&Quot; (3) "

Subtracting the equation (2) from the equation (3), the equation (4) can be derived.

&Quot; (4) "

Substituting Equation (3) into W in Equation (4), Equation (5) can be derived.

&Quot; (5) "

Here, Q_brine is a value calculated from Equation (1), COPc is a coefficient of performance of the heat pump at the time of cooling operation, and is a value supplied from the manufacturer of the heat pump.

Therefore, the demand side consumed heat quantity Q_load in the cooling operation can be calculated from the above equation (5).

Meanwhile, when the operation of the brine pump 60 is stopped, the calculation of the heat-source-side heat quantity Q_brine and the demand-side heat quantity Q_load is stopped.

As described above, in the present invention, by calculating the inflow temperature of the brine, the discharge temperature of the brine, and the flow rate of the brine corresponding to the heat source side and calculating and integrating the heat source-side heat quantity Q_brine in real time, The demand side consumed heat quantity Q_load can be calculated from the produced heat quantity Q_brine.

Therefore, since there is no need to measure the flow rate of the refrigerant corresponding to the demand side, there is no need to provide an expensive refrigerant flow meter, which is advantageous in that the demand side consumed heat quantity can be known at low cost.

Next, the heating operation in winter will be described.

The temperature Tg of the ground is lower than the temperature Tm of the machine room 21 during the winter and the temperature of the brine in and out of the heat pump 20 during operation of the heat pump 20 is higher than the outdoor temperature Therefore, the heat in the ground can be supplied to the heat pump 20.

Here, it is assumed that the machine room 21 is a space where a person can usually stay, and that the temperature is higher than the temperature Tg of the ground due to heat generated by a separate heating device or an internal mechanical device.

When the heating operation mode is selected by the user's operation, the control unit (not shown) turns on the brine pump 60. [

The heat pump 20 is not turned on when the brine pump 60 is turned on.

The inflow temperature Tin of the brine is measured by the first temperature sensor 81 from the time when the brine pump 60 is turned on and the discharge temperature Tout of the brine is measured by the second temperature sensor 82 .

Referring to FIG. 3, the temperature of the brine on the brine circulation channel 40 can be known when the brine pump 60 is driven.

The inlet temperature Tin of the brine and the outlet temperature Tout of the brine are substantially equal to or the same as the temperature Tm of the machine room 21 before the brine pump 60 is driven.

When the brine pump 60 is turned on, the discharge temperature Tout of the brine that has passed through the underground heat exchanger 10 gradually decreases to a temperature substantially equal to or lower than the temperature Tg of the ground.

Further, the brine inflow temperature (Tin) gradually decreases to a temperature substantially equal to or lower than the temperature (Tg) of the ground.

At this time, since the ground temperature Tg is higher than the outdoor temperature, the discharge temperature Tout of the brine from the underground heat exchanger 10 is higher than the brine inflow temperature Tin. That is, it can be seen that the heat pump 20 is off, but there is a temperature difference between the brine inflow temperature Tin and the discharge temperature Tout.

Thereafter, when the brine pump 60 is turned on, the heat pump 20 is turned on after a preset first set time t1.

The first set time t1 is about 2 minutes to 3 minutes, and the first set time t1 is set in the same manner as in the cooling operation.

When the heat pump 20 is turned on, the brine flowing into the heat pump 20 through the brine discharge passage 42 provides heat to the heat pump 20, (41) to the underground heat exchanger (10).

3, the inlet temperature Tin of the brine measured by the first temperature sensor 81 is lowered to a predetermined temperature while the heat pump 20 is being driven.

Further, the discharge temperature Tout of the brine measured by the second temperature sensor 82 also falls to a predetermined temperature. The brine having passed through the underground heat exchanger (10) passes through the outdoors and descends to a temperature lower than the ground, and enters the heat pump (20).

The difference between the inlet temperature Tin of the brine and the outlet temperature Tout of the brine is a difference in the amount of heat that provides the geothermal heat to the heat pump 20.

The heat source provided to the heat pump 20 is transferred to the refrigerant circulating in the refrigerant circulation channel 50 and supplied to the demand side heat exchanger 30. [

The refrigerant absorbs heat from the heat pump 20 and is then supplied to the demand side heat exchanger 30 via the refrigerant circulation flow path 50. The refrigerant is deprived of heat and condensed in the demand side heat exchanger 30 And then circulated to the heat pump 20 again.

Thereafter, when the stop of the heating operation mode is selected by the user's operation, the control unit (not shown) turns off the heat pump 20. At this time, the brine pump 60 is in the driving state.

3, when the heat pump 20 is turned off, it can be seen that the inlet temperature Tin and the discharge temperature Tout of the brine are substantially equal to or lower than the temperature Tg of the ground .

The brine pump 60 is turned off after a predetermined second set time? T2 after the heat pump 20 is turned off.

The control unit (not shown) does not turn off the heat pump 20 and the brine pump 60 at the same time. The brine pump 60 is further operated during the second set time period? T2 to take out the brine in the brine circulation channel 40 to the heat pump 20 side even after the heat pump 20 is turned off .

The second set time? T2 is set longer than the first set time? T1.

Since the temperature difference between the brine inlet temperature Tin and the discharge temperature Tout till the brine pump 60 is turned off even if the heat pump 20 is turned off, It is preferable to integrate the brine pump 60 until the brine pump 60 is turned off.

Meanwhile, a method of calculating the heat quantity of the brine-refrigerant type heat pump system during the winter heating operation as described above is as follows.

The control unit (not shown) calculates and integrates the heat-source-side heat quantity Q_brine in real time during heating operation from the time when the brine pump 60 is turned on until the brine pump 60 is turned off.

There is a temperature difference between the inflow temperature Tin and the discharge temperature Tout of the brine before the heat pump 20 is turned on after the brine pump 60 is turned on and the heat pump 20 is turned off Since the temperature difference between the brine inlet temperature Tin and the discharge temperature Tout exists before the brine pump 60 is turned off, the time for calculating the heat-source- 60) is operated.

In the heating operation, the heat-source-side heat quantity Q_brine is calculated and integrated in real time using the inflow temperature of the brine, the discharge temperature of the brine, the flow rate of the brine, and the specific heat of the brine.

Equation (6) is an equation for measuring the heat-source-side heat quantity Q_brine during the heating operation.

&Quot; (6) "

Here, ΔT is a difference value between the brine inflow temperature Tin measured by the first and second temperature sensors 81 and 82 and the brine discharge temperature Tout. The flow rate m of the brine is a value measured by the brine flow meter 70, and the specific heat C of the brine is a known value.

Using the equation (6), the heat source-side heat quantity Q_brine can be calculated and integrated in real time while the brine pump 60 is driven. In this embodiment, the integration is performed in units of seconds, for example.

On the other hand, a method of obtaining the demand side consumed heat quantity Q_load from the heat source side heat quantity Q_brine is as follows.

Equation (7) is an equation showing the relationship between the heat-source-side heat quantity Q_brine and the demand-side heat quantity Q_load according to the first law of thermodynamics.

&Quot; (7) "

Equation (8) represents the coefficient of performance (COPh) at the heating operation of the heat pump.

&Quot; (8) "

Subtracting Equation (7) from Equation (8), Equation (9) can be derived.

&Quot; (9) "

Substituting Equation (7) into W in Equation (9), Equation (10) can be derived.

&Quot; (10) "

Here, Q_brine is a value calculated from Equation (6), COPh is a coefficient of performance of the heat pump at the time of heating operation, and is a value supplied from the manufacturer of the heat pump.

Therefore, the demand side consumption heat quantity Q_load in the heating operation can be calculated from the above equation (10).

On the other hand, when the brine pump 60 is turned off, the calculation of the heat-source-side heat quantity Q_brine and the demand-side heat quantity Q_load is stopped.

As described above, in the present invention, by calculating the inflow temperature of the brine, the discharge temperature of the brine, and the flow rate of the brine corresponding to the heat source side and calculating and integrating the heat source-side heat quantity Q_brine in real time, The demand side consumed heat quantity Q_load can be calculated from the produced heat quantity Q_brine.

Therefore, since there is no need to measure the flow rate of the refrigerant corresponding to the demand side, there is no need to provide an expensive refrigerant flow meter, which is advantageous in that the demand side consumed heat quantity can be known at low cost.

It is also possible to set the time for calculating and integrating the heat source-side heat quantity Q_brine to the time when the brine pump 60 is turned on and off without reference to whether the heat pump 20 is driven, Calories can be calculated accurately.

While the present invention has been described with reference to exemplary embodiments, it is to be understood that the invention is not limited to the disclosed exemplary embodiments, but, on the contrary, is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims. Accordingly, the true scope of the present invention should be determined by the technical idea of the appended claims.

10: Underground heat exchanger 20: Heat pump
30: Demand side heat exchanger 40: Brine circulation flow path
50: Refrigerant circulation flow passage 60: Brine pump
70: brine flow meter 81: first temperature sensor
82: second temperature sensor

Claims (7)

A demand side heat exchanger provided with the heat source; a brine circulation flow path for connecting the underground heat exchanger and the heat pump to circulate the brine; A brine pump installed in the brine circulation channel inside the machine room for pumping the brine, a brine pump installed in the brine circulation channel inside the machine room to measure a flow rate of the brine A brine flowmeter, a first temperature sensor installed in the brine circulation channel inside the machine room and measuring an inflow temperature of the brine before entering the underground heat exchanger, a first temperature sensor installed in the brine circulation channel inside the machine room, And before entering the heat pump, the brine And a second temperature sensor for measuring a discharge temperature of the brine-refrigerant heat pump system,
Turning on the heat pump after the brine pump is turned on after a first set time;
Calculating and accumulating the heat quantity on the heat source side in real time using the inflow temperature of the brine, the discharge temperature of the brine, the flow rate of the brine, and the specific heat of the brine from the time when the brine pump is turned on;
Turning off the brine pump after a second set time after turning off the heat pump;
And stopping the accumulation of the heat-source-side heat quantity when the brine pump is turned off. The method according to claim 1,
When the calorific value on the heat source side is calculated,
(EN) A heat quantity calculation method of a brine - refrigerant heat pump system using a geothermal heat to calculate and integrate a demand - side consumed heat quantity using the heat - source - side heat quantity and the performance coefficient (COP) of the heat pump. The method according to claim 1,
Wherein the first set time uses geothermal heat set in accordance with an inflow temperature of the brine. The method according to claim 1,
The first set time period
Wherein a temperature of the brine is set to a time until a difference between an inflow temperature of the brine and a discharge temperature of the brine becomes equal to or less than a predetermined first temperature difference. The method according to claim 1,
Wherein the second set time period
Wherein the geothermal heat is set to a time until a difference between an inflow temperature of the brine and a discharge temperature of the brine becomes equal to or less than a preset second temperature difference. The method according to claim 1,
Wherein the second set time is set longer than the first set time. A demand side heat exchanger provided with the heat source; a brine circulation flow path for connecting the underground heat exchanger and the heat pump to circulate the brine; A brine pump installed in the brine circulation channel inside the machine room for pumping the brine, a brine pump installed in the brine circulation channel inside the machine room to measure a flow rate of the brine A brine flowmeter, a first temperature sensor installed in the brine circulation channel inside the machine room and measuring an inflow temperature of the brine before entering the underground heat exchanger, a first temperature sensor installed in the brine circulation channel inside the machine room, And before entering the heat pump, the brine And a second temperature sensor for measuring a discharge temperature of the brine-refrigerant heat pump system,
Turning on the heat pump after the brine pump is turned on after a first set time;
Calculating and accumulating the heat quantity on the heat source side in real time using the inflow temperature of the brine, the discharge temperature of the brine, the flow rate of the brine, and the specific heat of the brine from the time when the brine pump is turned on;
The method according to any one of claims 1 to 3, wherein the heat-source-side heat generated by the heat pump is calculated by using the heat-source-side heat produced by the heat pump and the coefficient of performance (COP) Calculation method of calorie of system.

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