JP5690650B2 - Geothermal characteristics analysis method and apparatus, soil heat source heat pump system operation adjustment method and apparatus, and program - Google Patents

Description

The present invention relates to a ground thermal characteristic analysis method and apparatus using a ground heat exchanger that circulates a heat medium, an operation adjustment method and apparatus for a soil heat source heat pump system, and a program.

In recent years, a soil heat source heat pump system that uses the ground as a heat source, circulates a heat medium in an underground heat exchanger, collects and dissipates heat with a heat pump, and supplies hot or cold to the load side has begun to be widely recognized. Unlike the atmosphere, the soil heat source heat pump system is stable with no significant changes throughout the year, so it has advantages such as energy saving, low running costs, and suppression of carbon dioxide (CO ₂ ) emissions. Further introduction is expected in the future.

  In order to operate the soil heat source heat pump system with high efficiency, for example, when used for air conditioning, the amount of heat released to the ground during cooling operation and from the ground during heating operation It is important to balance the amount of heat collected. As this type of technology, Patent Document 1 discloses that a ground heat exchanger and an auxiliary heat exchanger are used as heat sources, and the amount of ground heat collected by the heating load is equal to the amount of ground heat radiation by the cooling load. An air conditioning system using a ground heat exchanger that performs air conditioning by switching to an alternative is disclosed. Moreover, in patent document 2, the limit value of heat collection / radiation is set based on the exit temperature of the heat transfer water from the heat pump to the underground heat exchanger measured by the temperature sensor, and does not exceed the set limit value of heat collection / radiation. As described above, a heat pump device using geothermal heat that controls the operation of the heat pump is disclosed.

  In addition, the applicant of the present application discloses a soil heat source heat pump system in Patent Document 3 that uses a heat pump to circulate a heat medium in a ground heat exchanger using the ground as a heat source, collects and dissipates heat, and supplies hot or cold to the load side. Time-series change of heat load to be processed by the soil heat source heat pump system calculated using conditions including a heating period and a cooling period, ground environmental conditions, and specifications of the underground heat exchanger and heat pump Set the specifications of the soil heat pump system including the specifications of the above, simulate the operation of the soil heat source heat pump system, analyze the heat balance, and obtain the time series change of the temperature on the heat source side, According to the analysis procedure at the end of the cooling period of the next year and at least one of the start of the cooling period and the end of the heating period of the next year The simulation is repeated while changing at least one of the heat load to be processed by the soil heat source heat pump system and the specifications of the soil heat source heat pump system so that the temperature on the heat source side as a result of the simulation is substantially the same. A design method is proposed in which the heat load to be processed by the heat source heat pump system and the specification determination procedure for determining the specifications of the soil heat source heat pump system are proposed.

JP 2003-130494 A JP 2006-292310 A JP 2007-85675 A

  In order to operate the soil heat source heat pump system with high efficiency, for example, it is a problem to eliminate a long-term increase in underground temperature due to excessive cooling load (heat radiation) with respect to a heating load (heat collection). In this regard, if groundwater flow beyond the perceivable range can be expected, it is possible to suppress excessive heat radiation to the ground by the advection effect of groundwater and to add heat to the ground by adding a cooling tower etc. Reduction can be mentioned as a countermeasure.

  For groundwater flow, the groundwater flow velocity measurement method has been established to some extent, but there is still room for improvement in the accuracy of the measurement method, and the accumulation of data is small. It is difficult to incorporate groundwater effects at the design stage.

  On the other hand, if the simulation based on the analytical calculation model proposed in Patent Document 3 is applied, it is possible to grasp the ground thermal characteristics such as effective thermal conductivity using the underground temperature measurement data during the operation period. Is possible. Since the ground thermal characteristics obtained in this way are considered in consideration of groundwater flow, it is possible to reflect the effects of groundwater that is difficult to incorporate in the planning and design stages as described above in the operation stage. Become.

  The present invention has been made in view of the above points, and allows the ground heat characteristics to be ascertained at any time, and further, based on that, performs the operation and performance prediction of the soil heat source heat pump system, and the soil heat source heat pump system. The purpose is to be able to adjust the operating time and the amount of heat collected.

The ground thermal property analysis method of the present invention is a ground thermal property analysis method using a ground heat exchanger that circulates a heat medium , assuming an effective thermal conductivity as a ground thermal property value, and its effective conductivity. The first simulation procedure for calculating the time series change of the temperature on the heat source side using the calculation conditions measured every moment for a predetermined period, and the calculation of the temperature on the heat source side by the first simulation procedure Whether the change amount of the value from the initial underground temperature in the predetermined period and the change amount of the measured value of the temperature on the heat source side from the initial underground temperature in the predetermined period satisfy a predetermined condition the and a first determining step determines whether the calculated value of the variation between the first simulation variation and is by changing the effective thermal conductivity to the predetermined condition is satisfied in the measured value Repeating the procedure and the first determination procedure, And obtaining a satisfying effective thermal conductivity constant.
In addition, another feature of the ground thermal characteristic analysis method of the present invention is that the temperature on the heat source side is the outlet temperature of the underground heat exchanger, and in the first simulation procedure, the predetermined time period is sometimes changed. The ground heat exchanger inlet temperature and the circulating flow rate of the heat medium measured every moment are given as calculation conditions, the heat balance inside the underground heat exchanger and the heat conduction with the infinite surrounding ground are analyzed, and the temperature on the heat source side is calculated. Calculate the time series change of the outlet temperature of the underground heat exchanger.
The operation adjustment method in the soil heat source heat pump system of the present invention is scheduled based on the ground thermal characteristic analysis procedure for obtaining the effective thermal conductivity by the ground thermal characteristic analysis method of the present invention, and the integrated heat dissipation amount during the operation period. Resetting procedure to reset the operating heat load of the soil heat source heat pump system, the effective thermal conductivity by the ground thermal characteristics analysis procedure and the soil heat source heat pump system operating heat load by the resetting procedure, A second simulation procedure for executing a simulation of the operation of the soil heat source heat pump system to analyze a heat balance and calculating a time-series change in temperature on the heat source side, and a temperature on the heat source side according to the second simulation procedure A second determination procedure for determining whether or not the calculated value satisfies a predetermined temperature condition, and the heat source side Until the calculated value of the degree satisfies the predetermined temperature condition, the value related to the soil heat source heat pump system operation standard is changed and the second simulation procedure and the second determination procedure are repeated to satisfy the predetermined temperature condition It is characterized by obtaining a soil heat source heat pump system operation standard.
Further, another feature of the operation adjustment method of the soil heat source heat pump system of the present invention is an operation adjustment method of the soil heat source heat pump system combined with a secondary side (load side) auxiliary heat source machine, wherein the soil heat source The heat load of the heat pump system operation is an annual load amount, and the second simulation procedure and the second determination procedure are performed by changing the annual load amount until the calculated value of the temperature on the heat source side satisfies the predetermined temperature condition. The first heat radiation amount integrated value for stopping the operation of the soil heat source heat pump system, which is the soil heat source heat pump system operation standard, based on the annual load amount satisfying the predetermined temperature condition, or the soil Obtaining a second integrated heat extraction amount value for switching to combined operation of the heat source heat pump system and the secondary side auxiliary heat source machine .
In addition, another feature of the operation adjustment method of the soil heat source heat pump system of the present invention is an operation adjustment method of the soil heat source heat pump system combined with a primary side (heat source side) auxiliary heat source machine, the soil heat source heat pump The system operation heat load is an annual load amount, and until the calculated value of the temperature on the heat source side satisfies the predetermined temperature condition, the heat source side operating the primary side auxiliary heat source machine that is the soil heat source heat pump system operation standard The reference temperature that satisfies the predetermined temperature condition is obtained by changing the temperature (hereinafter referred to as a reference temperature) and repeating the second simulation procedure and the second determination procedure.
In addition, another feature of the operation adjustment method of the soil heat source heat pump system according to the present invention is that the heat demand and the cold demand are mixed, and the cold exhaust heat of the heating operation heat pump is cooled through a common heat source water pipe. Applying to the heat recovery system that mutually uses the heat exhaust heat of the cooling operation heat pump as the operating heat pump heat source for the heating operation heat pump heat source, and adjusting the operation of the soil heat source heat pump system that uses the primary auxiliary heat source machine in combination when the heat source is insufficient The one year is divided into a cooling period in which the cooling load is larger and a heating period in which the heating load is larger. In the cooling period, the cooling operation heat pump is replaced with the soil heat source heat pump system, and the heating operation heat pump cold exhaust heat. Treated as a primary side (heat source side) auxiliary heat source machine, and during the heating period, the heating operation heat pump is the soil heat source heat pump. Stem, said handle cooling operation the heat pump temperature exhaust heat as the primary-side auxiliary heat source machine, the soil source heat pump system operating heat load is annual load, the calculated temperature of the heat source side until the predetermined temperature condition is satisfied A value related to an operation standard of the soil heat source heat pump system is changed and the second simulation procedure and the second determination procedure are repeated to obtain an operation standard of the soil heat source heat pump system satisfying the predetermined temperature condition.
Further, another feature of the operation adjustment method of the soil heat source heat pump system of the present invention is that it is applied to a heat recovery system that recovers exhaust heat through a common heat source water pipe. An operation adjustment method of a soil heat source heat pump system that uses a side auxiliary heat source device together , the recovered exhaust heat is treated as an auxiliary heat source, the soil heat source heat pump system operation heat load is an annual load, and the temperature of the temperature on the heat source side Until the calculated value satisfies the predetermined temperature condition, the value related to the operation standard of the soil heat source heat pump system is changed, the second simulation procedure and the second determination procedure are repeated, and the predetermined temperature condition is satisfied. Determine the operating standards of the soil heat source heat pump system .
Further, another feature of the operation adjustment method of the soil heat source heat pump system of the present invention is that, in the predetermined temperature condition, the calculated value of the temperature on the heat source side according to the second simulation procedure is an upper limit value and a lower limit value. Or the condition that the upper limit value or the lower limit value is not exceeded.
In addition, another feature of the operation adjustment method of the soil heat source heat pump system of the present invention is that the predetermined temperature condition includes the aging in the calculated values of the maximum temperature and the minimum temperature on the heat source side according to the second simulation procedure. It includes a condition that both change values do not exceed a predetermined condition value.
Further, another feature of the operation adjustment method of the soil heat source heat pump system according to the present invention is that, for each unit period, the ground thermal characteristic analysis procedure, the resetting procedure, the second simulation procedure, and the first The soil heat source heat pump system operation standard is obtained by the determination procedure of 2, and the operation adjustment of the soil heat source heat pump system is executed based on the soil heat source heat pump system operation standard.

  According to the present invention, the effective thermal conductivity included in the influence of groundwater flow can be grasped at any time. Furthermore, the operation and performance prediction of the soil heat source heat pump system can be performed based on the effective thermal conductivity, and the operation time and the heat radiation amount of the soil heat source heat pump system can be adjusted. That is, it is possible to use the heat collection / radiation promotion effect by groundwater and the cooling / heating load imbalance elimination effect according to the actual situation.

It is a figure which shows schematic structure of the soil heat source heat pump system which can apply this invention. It is a figure which shows schematic structure of the control apparatus of the GSHP system to which this invention is applied. It is a flowchart which shows the process by a ground thermal characteristic analysis program. It is a characteristic view which shows the example which calculated | required the effective thermal conductivity by comparing the calculated value and measured value of an underground heat exchanger exit temperature. (A) is a figure which shows schematic structure of the system which combined the soil heat source heat pump system and secondary side (load side) auxiliary heat source machines, such as an air cooling chiller and a boiler, (b) is a soil heat source heat pump system and a primary side (heat source side) FIG. 2 is a diagram showing a schematic configuration of a system in combination with a cooling tower which is an auxiliary cooling heat source machine. It is a systematic diagram of a soil heat source heat pump system and a secondary side auxiliary heat source machine. It is a figure which shows the relationship of the load amount in each case of FIG. It is a flowchart which shows the process by the driving | operation adjustment program of the GSHP system in 1st Embodiment. It is a flowchart which shows the process by the geothermal operation evaluation program in 1st Embodiment. It is a flowchart which shows the confirmation process of long-term stability. It is a characteristic view which shows the example of the relationship between time and the amount of heat dissipation. It is a characteristic view which shows the example of the relationship between the GSHP system operation | movement heat load given as calculation conditions previously, and the GSHP system operation | movement heat load after reset. It is a characteristic diagram showing an example of the relationship between the underground heat exchanger outlet temperature calculated with the GSHP system operating heat load given as the calculation condition in advance and the underground heat exchanger outlet temperature calculated with the GSHP system operating heat load after resetting is there. It is a characteristic view which shows the example of the load amount in a commissioning unit period. It is a flowchart which shows the process by the driving | operation adjustment program of the GSHP system in 2nd Embodiment. It is a flowchart which shows the process by the geothermal operation evaluation program in 2nd Embodiment. It is a figure which shows the structural example which added the soil heat source heat pump system to the heat recovery system.

Preferred embodiments of the present invention will be described below with reference to the accompanying drawings.
(First embodiment)
FIG. 1 illustrates a schematic configuration of a soil source heat pump (Ground Source Heat Pump: GSHP) system 100 to which the present invention can be applied.
The GSHP system 100 includes a plurality of underground heat exchangers 101 buried in the ground, a heat pump 102 for collecting and radiating heat through a heat medium circulated through the various regional heat exchangers 101, and a heat pump 102. The main component is an air conditioner 103 that cools or heats the room via a cooled or heated heat medium.

In the GSHP system 100, with respect to the heat pump 102, the ground side (that is, the underground heat exchanger 101 side) that is the heat source is the primary side (heat source side), and the indoor side (that is, the air conditioner 103 side) is the secondary side ( (Load side). The amount of heat on the primary side is referred to as heat extraction / radiation amount, and the amount of heat on the secondary side is referred to as load amount.
Heat dissipation amount = cooling load amount + power consumption Heat extraction amount = heating load amount−power consumption. The relationship with the coefficient of performance COP is
COP = (cooling or heating) load amount / power consumption.

  FIG. 2 shows a schematic configuration of a control device 1 of the GSHP system that functions as a ground thermal characteristic analysis device to which the present invention is applied and an operation adjustment device of the GSHP system. Reference numeral 2 denotes an operation status analysis unit that analyzes the operation status of the GSHP system 100. Reference numeral 3 denotes a ground thermal characteristic analysis unit that analyzes the ground thermal characteristics. Reference numeral 4 denotes an operation adjustment unit that adjusts the operation of the GSHP system 100 in accordance with the operation status and the ground thermal characteristics. Specifically, the control device 1 of the GSHP system can be configured by a computer system including a CPU, a ROM, a RAM, and the like, and is realized by the CPU executing a program. Note that the control device 1 of the GSHP system may be configured by a single device or may be configured by a plurality of devices.

(Analysis of the operating status of the GSHP system)
In order to analyze the operation status of the GSHP system 100, as shown in FIG. 1, temperature sensors 104a and 104b are installed at the underground heat exchanger inlet and outlet, and a flow sensor 105 is installed at the underground heat exchanger outlet. Data collected from the sensors 104a, 104b, and 105 by the data logger is taken into the control device 1 of the GSHP system.

When the operating condition analysis unit 2 calculates the heat _{extraction /} dissipation amount q _p [W] from the underground, the heat _{extraction /} dissipation amount q _p from the underground is determined by the underground heat exchanger inlet / outlet temperatures T _pout and T _pin [° C.]. Using the circulation flow rate G _fp [m ³ / s] of the heat medium, it can be obtained by the following equation (1). c _pf is the constant-pressure specific heat [kJ / (kg · K)] of the heat medium, and ρ _f is the density [kg / m ₃ ] of the heat medium. Adopted when adopting heat radiation q _p from the ground is positive heat, the heat radiation amount is a negative value.

Further, when the operating state analysis unit 2 calculates the output q _hp [W] and COP of the heat pump 102, the temperature sensors 106 a and 106 b are provided at the primary side inlet / outlet of the heat pump 102, and the flow rate sensor 107 is provided at the primary side inlet of the heat pump 102. Is set. Moreover, wattmeters 108a and 108b for measuring the power consumption E of the heat pump 102 are installed. Output q _hp and COP of the heat pump 102, the primary-side inlet and outlet temperatures T _1out of the heat pump 102, T _1in [° C.], the circulation flow rate G _f1 of the heat medium [m ³ / s], using the power E [W], It can obtain | require by following Formula (2)-(4).

Note that when a negligible heat loss, etc. between the underground heat exchanger 101 and the heat pump _{102, T pin = T 1out,} T pout = T 1in, G fp = G f1 / n (n: a parallel circuit The number can be substituted for each other.

(Analysis of ground thermal characteristics)
An effective thermal conductivity is an example of the ground thermal characteristic value that most affects the GSHP system 100. The ground thermal characteristic analysis unit 3 calculates the effective thermal conductivity by the following calculation, and the effective thermal conductivity is a so-called apparent effective thermal conductivity, which includes the influence of groundwater flow.

  FIG. 3 is a flowchart showing processing by the ground thermal property analysis program in the ground thermal property analysis unit 3. If necessary, a subscript m is added to the actual measurement value, and a subscript c is added to the calculated value. First, calculation conditions are input (step S101). The calculation conditions are specifications such as the type, diameter, and length of the underground heat exchanger 101.

Next, an effective thermal conductivity λ _s [W / (m · K)] is assumed (step S102). Then, the actual value T _pinm of the time series change of the underground heat exchanger inlet temperature measured by the temperature sensor 104b and the actual value G _fpm of the time series change of the circulating flow rate of the heat medium measured by the flow sensor 105 are calculated. The simulation of the operation of the GSHP system 100 is executed by the analytical calculation model shown in the following equations (5) to (9) to analyze the heat balance, and the time series change T _poutc etc. of the underground heat exchanger outlet temperature is _calculated . Calculate (steps S103 to S106). The underground heat exchanger outlet temperature T _poutc is calculated based on a heat balance equation inside the underground heat exchanger as shown in equations (5) and (6). In addition, when heat is extracted from the ground, the ambient temperature of the underground heat exchanger 101 rises. Therefore, the surface temperature of the underground heat exchanger at that time can be expressed by equations (7) to (7) by applying infinite cylinder theory. Calculate according to 9). In this way, the analysis is performed in consideration of the natural recovery factor considering the heat conduction from the infinite surrounding ground. V _f is the volume of the heat medium [m ³ ], K _p-out is the heat flow rate outside the underground heat exchanger [W / (m ² · K)], and A _p-out is the outside of the underground heat exchanger. Area [m ² ], T _s is the soil temperature [° C.], r _p-out is the radius of the underground heat exchanger [m], and q ′ ₀ is the amount of heat released per unit area (heat flow) [W / m ² ]. , T ^* is a dimensionless temperature, t ^* is a Fourier number, τ is a variable related to time, β is an integration variable, J _x is a first-order Bessel function of x order, and Y _x is a Bessel function of second order of x order. .

Specifically, the ground heat exchanger surface temperature response is calculated based on the equation (9) (step S103). Next, the measured value T _{pinm of the} underground heat exchanger inlet temperature measured by the temperature sensor 104b and the measured value G _fpm of the circulating flow rate of the heat medium measured by the flow sensor 105 are given as calculation conditions (step S104). And underground heat exchanger exit temperature _Tpoutc is calculated based on Formula (5), (6) (step S105). Further, the surface temperature of the underground heat exchanger is calculated based on the equations (7) and (8) (step S106). These steps S103 to S106 are repeated until the end of the predetermined period (step S107) while the time t [h] is advanced (step S108). That is, the time series change T _poutc of the underground heat exchanger outlet temperature is calculated by giving the ground heat exchanger inlet temperature T _pinm and the circulating flow rate G _{fpm of the} heat medium measured as _moments as calculation conditions.

The amount of change (ΔT _poutc (t ₀ ) = T _poutc −T _s0 ) from the initial underground temperature T _s0 of the calculated value T _poutc of the underground heat exchanger outlet temperature obtained as a result of steps S103 to S108, and the actual measurement value The amount of change of T _{poutm from} the initial underground temperature T _s0 (ΔT _poutm (t ₀ ) = T _poutm −T _s0 ) is compared (step S109), and if the difference is sufficiently small, the assumed effective heat conduction The coefficient λ _s is adopted as the apparent effective heat conduction coefficient λ _a (step S110). If the difference is not sufficiently small, the effective thermal conductivity λ _s is changed (step S111), and the calculations and determinations of steps S103 to S109 are repeated.

For the calculation of the apparent effective thermal conductivity λ _a , the calculated value T _{poutc at the} last time and the actually measured value T _poutm are compared using all measured data for each elapsed period. In the example shown in FIG. 4, at an elapsed time of 200 [h], the underground heat exchanger outlet temperature T _poutc is calculated with an initial effective thermal conductivity of 1.5 [W / (m · K)]. When compared with the actual measurement value T _poutm , there is an error in both. Therefore, when the effective thermal conductivity is changed to 2.4 [W / (m · K)], it can be seen that the two substantially coincide. Therefore, the apparent effective thermal conductivity λ _a at this time is adopted as 2.4 [W / (m · K)].

On the other hand, at the elapsed time 540 [h], the calculated value T _poutc and the actually measured value T _poutm agree with each other under the condition of effective thermal conductivity 2.4 [W / (m · K)] at the elapsed time 200 [h]. It is gone. Therefore, when the effective thermal conductivity is changed to 3.01 [W / (m · K)], it can be seen that both coincide. Therefore, the apparent effective thermal conductivity λ _a at this time is adopted as 3.0 [W / (m · K)].

Although the actual value T _pinm of the time series change of the underground heat exchanger inlet temperature measured by the temperature sensor 104b was given as a calculation condition, the time series change of the underground heat exchanger inlet temperature is You may make it obtain | require with respect to a device exit temperature using the said Formula (1) using the load every moment, the performance characteristic of the heat pump 102, and the circulation flow rate of a heat medium.

(Operation adjustment of GSHP system)
The operation of the GSHP system 100 is adjusted based on the above-described operation status of the GSHP system 100 and the analysis of the ground thermal characteristics. Below, the unit period which adjusts driving | running | working by analyzing the operating condition and ground thermal characteristic of the GSHP system 100 is called a commissioning unit period, for example, 1 week is set.

In the present embodiment, as shown in FIG. 5A, a system in which a GSHP system 100 and a secondary side (load side) auxiliary heat source device 200 such as an air cooling chiller and a boiler are combined is considered. 6A to 6D are system diagrams of the GSHP system 100 and the secondary side auxiliary heat source unit 200. FIG. About the heat source capacity | capacitance of the GSHP system 100 and the secondary side auxiliary heat source machine 200, the following four cases are assumed.
(1) When the heat source capacities of both the GSHP system 100 and the secondary side auxiliary heat source unit 200 satisfy the peak load (see FIG. 6A).
(2) When only the heat source capacity of the GSHP system 100 satisfies the peak load (see FIG. 6B).
(3) When only the heat source capacity of the secondary side auxiliary heat source unit 200 satisfies the peak load (see FIG. 6C).
(4) When the heat source capacities of both the GSHP system 100 and the secondary side auxiliary heat source unit 200 do not satisfy the peak load (see FIG. 6D).
In addition, a heat source machine means the apparatus which manufactures the heat | fever required for air conditioning, hot water supply, etc. by the secondary side (load side). On the other hand, the heat source refers to the one that retains the heat that the heat source machine uses to produce heat, such as air, soil, and river water. In the GSHP system, a soil heat source heat pump (GSHP) is a heat source machine, and soil is a heat source. The air-cooled chiller or boiler is a device that compensates for the shortage of heat required on the secondary side manufactured by GSHP, which is a heat source device, and is therefore called a secondary side (load side) auxiliary heat source device.
On the other hand, since the cooling tower shown in FIG. 5B is a device that compensates for the heat shortage of the soil, which is a heat source, it is called a primary side (heat source side) auxiliary heat source machine. Moreover, what compensates for the lack of heat is not limited to an apparatus, and heat recovered from the exhaust water can also be used, so these are collectively referred to as an auxiliary heat source.

First, the case (1), as shown in FIG. 7 (a), the total loading of GSHP system 100 in Commissioning unit period (GSHP total load) Q _g meet can adopt heat radiation amount integrated value operation time When it exceeds, it is necessary to switch to the secondary side auxiliary heat source apparatus 200. The GSHP total load amount Q _g is obtained by the following equation (10) using the total load amount Q ₂ . Here, C is a correction coefficient that satisfies the integrated value of possible heat extraction, and the determination method will be described later. Further, the total load amount (auxiliary heat source total load amount) Q _Ass of the secondary side auxiliary heat source 200 is obtained by the following equation (11).

Also in the case (2), the GSHP total load amount Q _g is obtained by the equation (10). On the other hand, as shown in FIG. 7B, the load amount Q _g2 of the GSHP system 100 that must be operated simultaneously with the secondary side auxiliary heat source unit 200 is the peak load q _2max and the secondary side auxiliary heat source unit maximum. When the output q _Assmax is used, it is obtained by the following equation (12). Eventually, the load amount Q _g1 that the GSHP system 100 can operate with the total load is expressed by the following equation (13), and when it exceeds this, the combined operation with the secondary side auxiliary heat source device 200 is performed.

For case (3), as shown in FIG. 7 (c), similarly to the case 1, if it exceeds the operation time to meet the heat dissipation amount integrated value adopted can GSHP total load Q _g in commissioning unit period, It is necessary to switch to the secondary side auxiliary heat source machine 200.

In the case (4), as shown in FIG. 7D, first, it is necessary to assume the load amount Q _Ass1 of the secondary side auxiliary heat source device 200 generated due to insufficient output of the GSHP system 100. The load amount Q _Ass1 of the secondary side auxiliary heat source device 200 is obtained by the following equation (14) using the total load amount Q ₂ , the peak load q _2max, and the GSHP maximum output q _gmax . Therefore, the remaining auxiliary heat source load amount Q _Ass2 is _expressed by the following equation (15). On the other hand, the load amount Q _g2 of the GSHP system 100 when the output is reduced is expressed by the following equation (16). Consequently, the load amount Q _g1 that the GSHP system 100 can operate at the maximum load is expressed by the following equation (17). Sought by.

As described above, in the system corresponding to cases (1) and (3), it is necessary to determine the heat _extraction amount integrated value Q _pset1 for stopping the operation of the GSHP system 100. Adopted radiating amount integrated value Q _pset1 is, in the example of the case (1) shown in FIG. 7 (a), an adopted radiating amount when the driving GSHP system according to GSHP total load Q _g, then As shown, it is represented by the GSHP total load amount Q _g and the power consumption during the operation time. COP _ave is an average COP during the operation time.
Q _pset1 = Q _g + Q _g / COP _ave (when cooling)
Q _pset1 = Q _g -Q _g / COP _ave (during heating)

Further, in the system corresponding to cases (2) and (4), it is necessary to determine a heat _extraction amount integrated value Q _pset2 for switching to the combined operation with the secondary side auxiliary heat source device 200. In the case (2) shown in FIG. 7 (b), the integrated heat _removal amount Q _pset2 is the heat collection amount when the GSHP system is operated according to the load amount Q _g1 , as shown below. _Is expressed by the load amount Q _g1 and the power consumption during the operation time.
Q _pset2 = Q _g1 + Q _g1 / COP _ave (when cooling)
Q _pset2 = Q _g1 -Q _g1 / COP _ave (during heating)

In the geothermal operation evaluation program described below, the above calculation is performed with a COP that depends on the load and temperature that change from time to time, and Q _pset1 is calculated by accumulating in the commissioning unit period. The same _applies to Q _pset2 . The signs of the heat _extraction and heat collection integrated values Q _pset1 and Q _pset2 are + (plus) when heating _and- (minus) when cooling. In equation (18), i = 1 is attached below Σ and n is attached above Σ.
^{_{Q pset1 = Σ i = 1 n}} (Q gi + Q gi / COP i) ( during cooling)
Q _pset1 = Σ _{i = 1} ⁿ (Q _gi −Q _gi / COP _i ) (during heating) (18)

Based on the above, the operation adjustment method of the GSHP system 100 combined with the secondary side (load side) auxiliary heat source device 200 will be described. First, a geothermal operation evaluation program (hereinafter also referred to as CGC) incorporating the ground thermal characteristic analysis program shown in FIG. 3 will be described. FIG. 9 is a flowchart showing processing by the geothermal operation evaluation program. Initial conditions such as soil data, initial setting heating / cooling load, specifications of the GSHP system 100 including the specifications of the underground heat exchanger 101 and the specifications of the heat pump 102, the specifications of the secondary auxiliary heat source apparatus 200, the allowable temperature, the operation start date, etc. In the input state, as described in the flowchart of FIG. 3, using the measured values of the time series change of the underground heat exchanger outlet temperature, the inlet temperature, and the circulating flow rate of the heat medium from the start of operation to the present time, Apparent effective thermal conductivity λ _a is determined (step S301).

Next, during the heating operation, the integrated value Q _sm of the heat _extraction amount q _{p obtained} from the operation start time or the cooling / heating switching time t _sst obtained by the following equation (19) is the integrated estimated value Q _{sp of the} heat _extraction amount. It is determined whether or not (step S302). As a result, if Q _sm > Q _{sp is} not established, the process proceeds to step S306. If Q _sm > Q _sp , the process proceeds to step S303, the heating annual load predicted fluctuation value Q _2h is reset so as to be increased by Q _sm / Q _sp , and then the process proceeds to step S306. Similarly, during the cooling operation, it is determined whether or not the integrated value Q _sm of the heat _extraction amount q _p from the operation start time t _{sst is less} than the estimated integrated value Q _sp of the heat _extraction amount (step S304). As a result, if Q _sm > Q _{sp is} not established, the process proceeds to step S306. If Q _sm > Q _sp , the process proceeds to step S305, the cooling annual predicted load fluctuation value Q _2c is reset so as to be increased by Q _sm / Q _sp , and then the process proceeds to step S306.

Here, Q _2h and Q _2c are load times in a planned year (cooling period (for example, May 1 to October 31) + heating period (for example, November 1 to April 30)). It is fluctuation prediction data for every. On the other hand, Q _sm and Q _sp are integrated values of the heat extraction amount during the operation period from the start of the cooling or heating operation to the time point, and Q _sm is the integrated heat extraction amount value of the operation period from the start of the actual operation to the time point. (Refer to FIG. 11), Q _sp is a heat collection amount integrated predicted value for the operation period from the start of operation to that time. In steps S302 to S305, the operation period heat radiation amount integrated prediction value Q _sp calculated by the above equation (18) based on the annual load prediction fluctuation values Q _2h and Q _2c corrected by the previous CGC activation, Compared with the current operating period heat radiation integrated value Q _{sm of the} latest operation period, if the latter is large, the annual load predicted fluctuation values Q _2h and Q _2c and eventually the heat extracted integrated heat estimated value Q _sp are corrected by that ratio.

Next, the apparent effective thermal conductivity λ _a determined in step S301 is set (step S306), and the ground heat exchanger surface temperature response is calculated based on equation (9) (step S307). Next, a load for each GSHP time is determined based on the predicted annual load fluctuation values Q _2h and Q _2c (step S308), and the primary circulation flow rate is calculated (step S309). Next, the COP of the heat pump 102, the amount of heat extracted from the ground q _p , and the underground heat exchanger inlet temperature T _pin are calculated (step S310), and the underground heat exchange is performed based on the equations (5) and (6). The reactor outlet temperature T _pout is calculated (step S311), and the ground heat exchanger surface temperature is calculated based on the equations (7) and (8) (step S312). These steps S308 to S312 are repeated until the end of the commissioning unit period after the current time (step S313) while the time t is advanced (step S314).

Then, during the cooling operation, the underground heat exchanger outlet maximum temperature T _Poutmax is equal to or less than a predetermined setting value _T poutmaxset (step S315), if less than a predetermined setting value T _Poutmaxset The process proceeds to step S316. In step S316, the correction coefficient C satisfying the possible heat extraction amount integrated value is reset, the cooling annual load predicted fluctuation value Q _2c is reset, and the process returns to step S308. That is, with respect to the correction coefficient C that satisfies the possible heat radiation integrated value, for the cooling period, the maximum underground heat exchanger outlet temperature T _poutmax obtained by calculation with respect to the load condition exceeds a predetermined set value T _poutmaxset. The performance prediction calculation is performed again. In this case, the correction coefficient C is calculated by the following equation (20). T _s0 is the initial underground temperature, and S is the safety factor.

If the maximum temperature T _poutmax is equal to or lower than the predetermined set value T _poutmaxset in step S315, the process proceeds to step S317. In step S317, it is determined whether or not the amount of change of the maximum temperature T _{poutmax from} the initial underground temperature T _s0 satisfies the condition shown in the following expression (21). If not, the process proceeds to step S318. In step S318, the correction coefficient C satisfying the possible heat extraction amount integrated value is reset, the cooling annual load predicted fluctuation value Q _2c is reset, and the process returns to step S308. That is, for the correction coefficient C that satisfies the possible heat _extraction integrated value, for the cooling period, the maximum underground heat exchanger outlet temperature T _poutmax obtained by calculation with respect to the load condition is the condition shown in the following equation (21). When it does not satisfy, it is calculated, and the performance prediction calculation is performed again. In this case, the correction coefficient C is calculated by the following equation (22).

Also, during the heating operation, the underground heat exchanger outlet lowest temperature T _Poutmin it is determined whether a predetermined set value T _Poutminset more (step S319), if a predetermined set value T _Poutminset more steps The process proceeds to S320. In step S320, the correction coefficient C satisfying the possible heat extraction amount integrated value is reset, the heating annual load predicted fluctuation value _Q2h is reset, and the process returns to step S308. That is, with respect to the correction coefficient C that satisfies the possible heat removal amount integrated value, for the heating period, when the underground heat exchanger outlet minimum temperature T _poutmin obtained by calculation with respect to the load condition is below a predetermined set value T _poutminset The performance prediction calculation is performed again. In this case, the correction coefficient C is calculated by the following equation (23).

If the minimum temperature T _poutmin is equal to or higher than the predetermined set value T _poutminset in step S319, the process proceeds to step S321. In step S321, it is determined whether or not the amount of change from the initial underground temperature T _s0 of the minimum temperature T _poutmin satisfies the condition shown in the following expression (24). If not, the process proceeds to step S322. In step S322, the correction coefficient C satisfying the possible heat extraction amount integrated value is reset, the heating annual load predicted fluctuation value _Q2h is reset, and the process returns to step S308. That is, with respect to the correction coefficient C that satisfies the possible heat radiation integrated value, for the heating period, the minimum underground heat exchanger outlet temperature T _poutmin obtained by calculation with respect to the load condition satisfies the condition shown in the following equation (24). When it does not satisfy, it is calculated, and the performance prediction calculation is performed again. In this case, the correction coefficient C is calculated by the following equation (25). The safety factor S is given, for example, 0.02.

As described above, in steps S315 to S322, the underground heat exchanger outlet temperature T _pout is estimated, and when the value exceeds the upper and lower limit values, the heat _{extraction /} radiation amount integrated values Q _pset1 and Q _pset2 are obtained. The necessary annual load forecast fluctuation values Q _2h and Q _2c are reset.

Next, in step S323, long-term stability is confirmed. FIG. 10 is a flowchart showing the long-term stability confirmation processing in step S323. The GSHP time load is determined (step S401), and the primary circulation flow rate is calculated (step S402). Next, the COP of the heat pump 102, the amount of heat radiated from the ground q _p , and the underground heat exchanger inlet temperature T _pin are calculated (step S403), and the underground heat exchange is performed based on the equations (5) and (6). The reactor outlet temperature T _pout is calculated (step S404), and the ground heat exchanger surface temperature is calculated based on the equations (7) and (8) (step S405). Next, the monthly heat radiation amount is calculated (step S406), and it is confirmed whether or not the remainder of t ÷ 730 (730: a value obtained by dividing one year 8760 hours by 12 months) is 0 (step S407). The monthly integrated heat radiation amount is stored (step S408). These steps S401 to S408 are repeated until time t = t _end1 (end time of operation years + 1 year (year during operation)) while the time t is advanced (step S410) (step S409). In steps S401 to S410, calculation up to the year of operation is performed, and a monthly heat removal amount for long-term prediction is calculated.

Next, determine the GSHP monthly adopting heat radiation amount (step S411), COP of the heat pump 102, adopted heat radiation q _p from the ground, the underground heat exchanger inlet temperature T _pin calculated (step S412), the formula ( 5) The ground heat exchanger outlet temperature T _pout is calculated based on (6) (step S413), and the ground heat exchanger surface temperature is calculated based on equations (7) and (8) (step S414). ). These steps S411 to _{S414 are} repeated until time t = _tend2 (the number of years of operation + the end time of the year to be predicted) while the time t is advanced (step S416) (step S415). In steps S411 to S416, calculations up to the number of years for which prediction is desired are performed.

Then, x-th year of underground heat exchanger outlet maximum temperature T _Poutmax and _(x) a (x + 4) the difference is a predetermined condition of the th year of underground heat exchanger outlet maximum temperature _T poutmax _{(x + 4)} filled, and, x-th year of underground heat exchanger outlet lowest temperature T _Poutmin and _{(x) (x} + ₄₎ the difference is a predetermined condition of the th year of underground heat exchanger outlet lowest temperature _T poutmin _{(x + 4)} Then, the correction coefficient C satisfying the integrated value of the possible heat extraction amount is reset so that the heating annual load predicted fluctuation value Q _2h and the cooling annual load predicted fluctuation value Q _2c are reset (steps S417 to S421). The predetermined condition here is that the difference in the first to fifth years is 0.5 [° C.], and the difference in the sixth to tenth years is 0.25 [° C.]. Note that the process of step S323 may not be performed every time in the flowchart of FIG. 9, and may be performed once every several times (about once a month).

Returning to FIG. 9, in step S324, the heat _extraction amount integrated value Q _pset1 for stopping the operation of the GSHP system 100 or the heat _extraction amount integration for switching to the combined operation with the secondary side auxiliary heat source device 200 is performed. The value Q _pset2 is determined. In addition, the heat collection amount integrated value Q _pset3 that activates the CGC first is determined during the period in which the operation adjustment of the GSHP system 100 is performed.

Here, the integrated heat radiation amount values Q _pset1 and Q _pset2 are the integrated values of the heat _{extraction amounts} in the commissioning unit period. _Q2hcom or _Q2ccom is defined as a commissioning unit period load amount in which the period of time is equal to the amount of heat _extraction and heat radiation integrated value _Qpset1 , _Qpset2 (see FIG. 14). In addition, there can be a negative value in the amount of heat release due to the cooling operation. This is fluctuation data obtained by extracting the load in the next commissioning unit period from the reset annual predicted load fluctuation values Q _2h and Q _2c . Then, if these Q _2hcom and Q _2ccom are _defined as Q _g in equation (18), Q _pset1 and Q _pset2 are derived.

As described above, the integrated heat collection / dissipation value Q _pset1 and Q _pset2 must be calculated annually because it is necessary to calculate the maximum underground heat exchanger outlet temperature during the cooling period or the minimum underground heat exchanger outlet temperature during the heating period. Perform simulation and set based on it. That is, as shown in FIG. 12, the GSHP system operating heat load given as a calculation condition in advance, ie, the annual load predicted fluctuation values Q _2h and Q _2c (annual load Q _{2 in} FIG. 12) given first are actually GSHP system operation heat load (annual load predicted fluctuation values Q _2h , Q _2c ) is reset based on the operation data from the start of operation to the present time, that is, the integrated heat removal amount Q _sm (see FIG. 12). Load Q ₂ ′) (steps S302 to S305) and an annual operation simulation are performed. Then, as shown in FIG. 13, when the underground heat exchanger outlet temperature T _pout exceeds the upper and lower limit values, the annual load predicted fluctuation values Q _2h and Q _2c are reset so as to be within the upper and lower limit values. (Steps S315, S316, S319, S320). Finally, as shown in FIG. 14, if the commissioning unit period is, for example, the elapsed time 846 to 1014h from the start of operation, the heat _extraction amount in this period obtained by the operation simulation is Q _pset1 and Q _pset2 . Note that the actual system configuration is one of cases (1) to (4) in FIGS. Therefore, what is substantially determined is either the Q _pset1 and Q _pset2. The larger value that cannot be reached is set for the value that cannot be obtained.

In addition, the heat _{extraction /} radiation amount integrated value Q _pset3 is calculated by calculating the heat extraction / radiation amount for the four days of the week when the heating load integrated value and the cooling load integrated value for heating and cooling respectively peak during the simulation. .

In the geothermal operation evaluation program thus configured, it is possible to calculate Q _pset1 or Q _pset2 that is the GSHP operable amount in the next commissioning unit period. The GSHP operable amount is calculated by predicting the primary side temperature within each period of cooling and heating, and the GSHP system 100 can secure a predetermined output, and an upper limit temperature (during cooling) that can ensure higher efficiency than other heat source units, It is calculated by convergence calculation so as to be within the lower limit temperature (during heating). That is, when there is a surplus capacity, it is increased, and when there is a possibility of output shortage and efficiency deterioration within the period, it is decreased.

  The long-term judgment for absorbing load imbalance, which was postponed to the next fiscal year by confirming the long-term stability in step S323, is similar to the convergence after the load data is roughly reduced to the monthly fluctuation data. It is made possible by performing calculations over several years.

Next, FIG. 8 is a flowchart showing processing by the operation adjustment program of the GSHP system. The CGC shown in FIG. 9 is incorporated as a subprogram of this operation adjustment program, and periodically activates the CGC to determine a heat extraction amount integrated value capable of operating the GSHP system in the next commissioning unit period. The operation adjustment program outputs the underground heat exchanger inlet / outlet temperature, circulation flow rate, integrated value of the heat _extraction / cooling period, etc. to the CGC, and the integrated heat _extraction amount Q _pset1 from the calculation result of the CGC. Q _pset2 and Q _pset3 are received.

First, the CGC is activated immediately after the start of operation, and the heat radiation amount integrated value Q _pset3 that activates the CGC next time is determined (step S201).

Next, the ground heat exchanger inlet / outlet temperatures T _pout and T _pin measured by the temperature sensors 104a and 104b and the circulating flow rate G _{fp of the} heat medium measured by the flow sensor 105, which are data necessary for commissioning, are obtained. (step S202), obtained by the above equation (1) the adoption heat radiation q _p from the ground (step S203). Then, the cooling / heating period heat radiation amount integrated value Q _sm is obtained by the above equation (19), and the commissioning unit period integrated value Q _cm is obtained by the following equation (26) (see FIG. 11) (step S204).

Next, during the heating operation, it is determined whether or not the commissioning unit period integrated value Q _cm exceeds the heat _extraction amount integrated value Q _pset1 (step S205). As a result, if Q _cm > Q _pset1 , the process proceeds to step S208. If Q _cm > Q _pset1 , the process proceeds to step S207, where the GSHP system 100 is stopped and the secondary side (load side) auxiliary heat source unit 200 is activated to start operation (or the secondary side auxiliary heat source unit 200). Then, the operation proceeds to step S208. On the other hand, during the cooling operation, it is determined whether or not the commissioning unit period integrated value Q _cm is _less than the heat _extraction amount integrated value Q _pset1 (step S206). As a result, if Q _cm <Q _{pset1, the process} proceeds to step S209. If Q _cm <Q _pset1 , the process proceeds to step S207, where the GSHP system 100 is stopped and the secondary side auxiliary heat source device 200 is started to start operation (or the operation of the secondary side auxiliary heat source device 200 is promoted). After that, the process proceeds to step S208.

Next, at the time of heating operation, it is determined whether or not the commissioning unit period integrated value Q _cm exceeds the heat _extraction amount integrated value Q _pset2 (step S208). As a result, if Q _cm > Q _{pset2 is} not _reached , the process proceeds to step S211. If Q _cm > Q _pset2 , the process proceeds to step S210, and after switching to the operation based on the secondary side auxiliary heat source apparatus 200, the process proceeds to step S211. On the other hand, during the cooling operation, it is determined whether or not the commissioning unit period integrated value Q _cm is _less than the heat _extraction amount integrated value Q _pset2 (step S209). As a result, if Q _cm <Q _pset2 , the process proceeds to step S211. If Q _cm <Q _pset2 , the process proceeds to step S210, and after switching to the operation based on the secondary side auxiliary heat source apparatus 200, the process proceeds to step S211. In addition, since the larger value that cannot be actually reached is set as the value that cannot be obtained from Q _pset1 and Q _pset2 , step S205 and step S208, and step S206 and step S209 cannot be Yes at the same time. .

These steps S202～S210, while advancing time t by a predetermined time step Delta] t (step S212), and repeats until the time t = t _next (step S211). For example, initially, 1 hour is set, and Δt is set to 1 minute, that is, 1/60 hours. t increases to 1/60, 2/60, 3/60,... each time it goes to the return loop, and when 60/60 = 1 hour is reached, t = t _next and the next step Proceeding to S213, the underground heat exchanger inlet / outlet temperature and circulating flow rate at that time are stored.

Next, at the time of heating operation, it is determined whether CGC has not been started after switching to the cooling / heating operation, and whether the heat _{extraction /} radiation amount integrated value Q _sm exceeds the heat _{extraction /} radiation amount integrated value Q _pset3 (step S214). As a result, if the CGC is not started after switching to the cooling / heating operation and Q _sm > Q _{pset3, the process} proceeds to steps S217, S219, and S220. If CGC has not been started after switching to the cooling / heating operation and Q _sm > Q _pset3 , the process proceeds to step S216, where CGC is started to determine the heat _removal amount integrated values Q _pset1 and Q _pset2 in the next commissioning unit period. In addition, after the commissioning unit period integrated value Q _cm is initialized, the process proceeds to steps S217, S219, and S220. On the other hand, at the time of the cooling operation, it is determined whether CGC has not been started after switching to the cooling / heating operation, and whether the heat _{extraction /} radiation amount integrated value Q _sm is lower than the heat _{extraction /} radiation amount integrated value Q _pset3 (step S215). As a result, if the CGC is not started after switching to the cooling / heating operation and Q _sm <Q _{pset3 is} not established, the process proceeds to steps S217, S219, and S220. If CGC has not been started after switching to the cooling / heating operation and Q _sm <Q _pset3 , the process proceeds to step S216, where the CGC is activated to determine the integrated heat _removal amount Q _pset1 and Q _pset2 in the next commissioning unit period. In addition, after the commissioning unit period integrated value Q _cm is initialized, the process proceeds to steps S217, S219, and S220.

After the cooling / heating operation is switched, if the load is too small, the evaluation by CGC is not effective. Therefore, in steps S214 and S215, the CGC is not started until the integrated heat radiation amount Q _sm during the cooling (heating) period reaches Q _pset3 . That is, the switching determination from the running period to the full-fledged autonomous control period is performed.

Next, when the CGC has been started after switching to the heating / cooling operation (step S219), the operation time of the GSHP system 100 is 1 hour or longer (step S217), and the CGC is not started on the commissioning designated day (step S220) ( In step S218), the process proceeds to step S221, where the CGC is activated to determine the heat radiation amount integrated values Q _pset1 and Q _pset2 and initialize the commissioning unit period integrated value Q _cm .

In steps S217, S219, and S220, the CGC after the commissioning unit period elapses after the heat _extraction integrated value Q _sm reaches Q _pset3 , that is, in light of the CGC start-up conditions after entering full-scale autonomous control operation. Judgment to start up. The central activation condition is “CGC not activated on commissioning designated day” in step S220. If Monday is the designated day, Tuesday, Wednesday, ... until the day, CGC is activated on the previous Monday, so No, but if the next Monday comes, it will be Yes if CGC is not activated, step Proceeding to S221, CGC is activated. In step S217, “GSHP system operation time of 1 hour or more”, because the load of the GSHP system 100 is too small and the GSHP system 100 repeatedly starts and stops, the error in the calculation of the apparent effective thermal conductivity tends to increase. Since it cannot be said that the evaluation by the CGC is effective, the CGC is not activated in that case. In step S219, “CGC activated after switching to cooling / heating operation” has confirmed whether or not steps S214 and S215 have been performed. Note that the commissioning unit period is assumed to be one week. However, when changing this, if the unit period is set to 10 days instead of the commissioning specified day in the determination of step S220, the commissioning specified day is set to 10. It becomes correspondence such as making it the day of multiple.

Next, while confirming whether the remainder of t ÷ 730 (730: a value obtained by dividing 8730 hours of one year by 12 months) becomes 0 (step S222), the monthly integrated heat radiation amount is stored (step S223). ). Further, at the time of switching between the cooling and heating operations (step S224), the heat radiation amount integrated value Q _sm is initialized (step S225).

These steps S202～S225, increments the t _next with advancing time t predetermined time by step Δt is repeated (step S226). That is, in steps S202 to 213, the underground heat exchanger inlet / outlet temperature and circulation flow rate are stored every other hour.

As described above, the CGC is activated on the commissioning designated day set in advance, and the heat radiation amount integrated values Q _pset1 and Q _pset2 are determined. Geothermal heat is a stable heat source as long as it operates while monitoring temperature changes, and it does not have to be controlled in accordance with short-term load fluctuations. Therefore, the control during one commissioning unit period can be sufficiently handled by one stop or switching control.

  As described above, the operation status and ground thermal characteristics of the GSHP system 100 are ascertained at any time, and the operation and performance prediction of the GSHP system 100 are performed based on the operation status, and the operation time and heat extraction amount of the GSHP system 100 are adjusted. Can do.

  In this case, the effective thermal conductivity and load fluctuation are reviewed for each relatively short commissioning unit period, and the ground until the next commissioning unit period is set so that the primary temperature falls within the upper and lower limits based on the revised values. The amount of medium heat available can be calculated and controlled. Therefore, for example, as described in Patent Document 2, instead of sequentially controlling so as not to exceed the heat extraction limit value, it is possible to cope with a certain amount of load during the same period, for example, in the first half of the season. If there are few, it becomes possible to promote the use in the second half.

(Second Embodiment)
In 2nd Embodiment, as shown in FIG.5 (b), the system which combined the GSHP system 100 and primary side (heat source side) auxiliary heat source machines, such as a cooling tower and an auxiliary heat source boiler, is considered. Here, the system which combined the cooling tower 300 which is a primary side auxiliary | assistant cooling-heat source machine is illustrated. When performing the operation control of the cooling tower 300, measurement of the temperature of the cooling tower system is not particularly necessary, performed on the basis of the measured data of the underground heat exchanger outlet temperature T _out as shown in FIG.

When the cooling tower 300 is combined, as in the first embodiment, switching to the combined operation with the heat collection / radiation amount integrated value Q _pset1 for stopping the operation of the GSHP system 100 and the secondary side auxiliary heat source device 200 is performed. The ground heat exchanger outlet temperature T _poutset for starting the operation of the cooling tower 300 is set as a reference temperature instead of setting the heat _{extraction /} radiation amount integrated value Q _pset2 .

  Hereinafter, the operation adjustment of the GSHP system 100 combined with the cooling tower 300 will be described. First, CGC combining the ground thermal characteristic analysis program shown in FIG. 16 will be described. FIG. 16 is a flowchart showing processing by the geothermal operation evaluation program. In addition, it demonstrates centering around difference with FIG. 9 of 1st Embodiment, and abbreviate | omits detailed description about the same process.

Steps S601 to S613 are the same as steps S301 to S313 in FIG. It is determined whether or not the underground heat exchanger outlet maximum temperature T _poutmax during the cooling period is equal to or _lower than a predetermined set value T _poutmaxset or whether the temperature condition T _poutset is lower than 20 [° C.] (step S615). . If neither condition is satisfied, the process proceeds to step S616. In step S616, the reference temperature T _poutset is lowered by 1 [° C.] and the process returns to step S608.

If the maximum temperature T _poutmax is equal to or _lower than the predetermined set value T _poutmaxset or the temperature condition T _poutset falls below 20 [° C.], the process proceeds to step _S617 . In step _S617 , whether or not the amount of change of the maximum temperature T _{poutmax from} the initial underground temperature T _s0 satisfies the condition shown in the following expression (27), or whether the temperature condition T _poutset exceeds 35 [° C.]. Determine whether. If neither condition is satisfied, the process proceeds to step S618. In step _S618 , the reference temperature T _poutset is _increased by 1 [° C.], and the process returns to step S608.

In step S619, long-term stability is confirmed. This process is similar to FIG. 10, as the difference, the T _Poutset raised 1 [° C.] in step S421, is that the lower 1 [° C.] The T _Poutset in step S425.

In step S620, a heat _extraction amount integrated value Q _pset3 that activates the CGC first is determined during a period in which operation adjustment of the GSHP system 100 is performed.

Next, FIG. 15 is a flowchart showing processing by the operation adjustment program of the GSHP system. In addition, it demonstrates centering around difference with FIG. 8 of 1st Embodiment, and abbreviate | omits detailed description about the same process. The operation of the cooling tower is started when the underground heat exchanger outlet temperature T _pout during the cooling period exceeds the reference temperature T _poutset (steps S507 and S508). That is, the cooling tower 300 is operated while T _pout > T _poutset .

In addition, when the cooling tower 300 has a backup function that can cover 100% of the cooling load, the power consumption of the fan power and the like increases according to the capacity, so the backup operation time Except for the belt, it is necessary to reduce the output (fan speed, etc.). Therefore, except for conditions that require the output of the cooling tower 300 to be extremely low such that the reference temperature T _poutset is lower than 20 [° C.], the cooling tower 300 is not set to the maximum output operation, and the rotational speed of the fan is set. The operation to be suppressed is performed (steps S505 and S506).

  In addition, also when using the auxiliary | assistant heat source boiler which is a primary side (heat source side) auxiliary | assistant heat source machine, the underground heat exchanger exit temperature setting of FIG. 15 changes, and the upper limit of step S615 of FIG. 16, S617 becomes a lower limit. It is almost the same except for changes. Moreover, it is also possible to use a primary / secondary auxiliary heat source device for cooling and heating as in the case of the secondary (load side) auxiliary heat source device.

(Third embodiment)
For example, when there is a mixture of hot and cold demand due to hot water supply and cooling, a heat recovery system that builds a heat recovery loop that uses the mutual exhaust heat is effective. In the heat recovery system, energy can be saved by mutually using the warm exhaust heat of the cooling for hot water supply and the cold exhaust heat of the hot water supply for cooling. However, the thermal demand and the cold demand do not always exist at the same time, and there is a time difference in the exhaust heat, so in fact, the heat source water piping is used as the main pipe in the building, and the auxiliary heat source according to the balance difference in the cold and exhaust heat (Auxiliary boiler, cooling, etc.) is operated, heat source water is maintained in a medium temperature range (about 10 to 30 [° C.]) where the heat pump can be operated with high efficiency, and heat is collected or radiated therefrom.

  In the example shown in FIGS. 17A and 17B, the heat demand and the cold demand are mixed, and the cold exhaust heat of the heating operation heat pump is used as the cooling operation heat pump heat source via the common heat source water pipe. It is a heat recovery system that mutually uses the exhaust heat from the heat source as a heat pump heat source for heating operation. In this way, by utilizing the heat storage property of the ground and adding the GSHP system to the heat source water piping of a general heat recovery system, it is possible to store the excess cold heat exhaust heat generated due to the balance difference of the cold heat exhaust heat in the ground. . By storing heat in the ground, the time difference between cold and hot demand can be absorbed, the operation of the auxiliary heat source can be minimized, and further energy saving can be achieved. In a heat pump system that mixes cooling and heating heat sources, that is, cold exhaust heat, if heat balance analysis is performed to exchange surplus cold exhaust heat generated due to the balance difference with the ground, optimal use of cool heat is possible in season units, not sequentially. A possible heat recovery system can be operated. When the present invention is applied to such a heat recovery system, one year is divided into a cooling period in which the cooling load is larger and a heating period in which the heating load is larger. In the cooling period, the cooling operation heat pump is replaced with the soil heat source heat pump system, heating The operating heat pump cold exhaust heat is treated as a primary side (heat source side) auxiliary heat source machine, and the heating operation heat pump is treated as a soil heat source heat pump system and the cooling operation heat pump temperature exhaust heat is treated as a primary side auxiliary heat source machine in the heating period. The exhaust heat of the heat pump handled as the primary side auxiliary heat source machine is not the original purpose of generating exhaust heat, but it becomes the source of the final heat, so if the heat source is insufficient, the primary side auxiliary heat source machine (cooling tower, auxiliary heat source boiler) Etc.) is required.

  The example shown in FIG. 17C is a heat recovery system that performs exhaust heat recovery via a common heat source water pipe, and treats the recovered exhaust heat as an auxiliary heat source. In the illustrated example, waste heat from a kitchen or bathroom, heat recovered by a solar heat collector, exhaust heat from a fuel cell, and the like are handled as auxiliary heat sources. In this way, waste heat from kitchens and bathrooms, recovered heat from solar collectors, exhaust heat from fuel cells, etc. can be further increased if heat balance analysis is performed by adding waste heat specifications (temperature, flow rate, amount of heat, etc.). Efficient operation is possible. In addition, since an auxiliary heat source becomes a final heat source, when the heat source is insufficient, it is necessary to operate a primary side (heat source side) auxiliary heat source machine (a cooling tower, an auxiliary heat source boiler, etc.).

  In addition, although it is the same as primary heat | fever (heat source side) auxiliary heat source machines, such as a cooling tower shown in 2nd Embodiment, cold heat exhaust heat of a heat pump, hot water supply exhaust heat, fuel cell exhaust heat, etc. act. However, none of them adjust the output as a heat source, and the use of heat is intended for use, so it is used together with the primary side auxiliary heat source equipment such as a cooling tower, and the operation adjustment flow is managed by the amount of heat extracted from the underground heat. This is in accordance with the first embodiment. In this case, a primary side auxiliary heat source device is used in combination with the first heat radiation amount integrated value for stopping heat radiation from the ground heat exchanger of the soil heat source heat pump system, and the ground heat exchanger of the soil heat source heat pump system. A second heat radiation amount integrated value for performing heat radiation from the auxiliary heat source is obtained.

  1: control device of soil heat source heat pump system, 2: operating condition analysis unit, 3: ground heat characteristic analysis unit, 4: operation adjustment unit, 100: soil heat source heat pump system, 101: underground heat exchanger, 102: heat pump, 103: Air conditioner, 104a, 104b, 106a, 106b: Temperature sensor, 105, 107: Flow rate sensor, 108a, 108b: Wattmeter

Claims (16)

Geothermal heat characteristic analysis method using underground heat exchanger that circulates heat medium ,
Assuming an effective thermal conductivity as the ground thermal characteristic value, a first time series is used to calculate a time-series change in temperature on the heat source side using a calculation condition measured every moment for a predetermined period using the effective conductivity. And the simulation procedure of
The amount of change from the initial underground temperature in the predetermined period of the calculated value of the temperature on the heat source side according to the first simulation procedure , and the initial underground temperature in the predetermined period of the measured value of the temperature on the heat source side And a first determination procedure for determining whether or not the amount of change from the first condition satisfies a predetermined condition,
The variation of the calculated value and the change amount of the measured value by changing the effective thermal conductivity to the predetermined condition is satisfied repeat the first simulation procedure and the first determining step, said predetermined condition A method for analyzing ground thermal characteristics, characterized by obtaining an effective thermal conductivity satisfying the above condition. The temperature on the heat source side is the underground heat exchanger outlet temperature,
In the first simulation procedure, the ground heat exchanger inlet temperature and the circulating flow rate of the heat medium measured every moment during the predetermined period are given as calculation conditions, the heat balance inside the underground heat exchanger, infinite surroundings The ground thermal characteristic analysis method according to claim 1, wherein the heat conduction with the ground is analyzed, and the time-series change of the underground heat exchanger outlet temperature is calculated as the temperature on the heat source side. A ground thermal property analysis procedure for obtaining an effective thermal conductivity by the ground thermal property analysis method according to claim 1 or 2,
A resetting procedure for resetting the planned soil heat source heat pump system operating heat load based on the accumulated heat removal amount during the operation period;
Using the effective thermal conductivity by the geothermal thermal characteristic analysis procedure and the soil heat source heat pump system operation heat load by the resetting procedure, a simulation of the operation of the soil heat source heat pump system is performed for the unit period after the current time, and the heat balance And a second simulation procedure for calculating a time-series change in temperature on the heat source side,
A second determination procedure for determining whether the calculated value of the temperature on the heat source side according to the second simulation procedure satisfies a predetermined temperature condition,
Until the calculated value of the temperature on the heat source side satisfies the predetermined temperature condition, the value related to the soil heat source heat pump system operation standard is changed and the second simulation procedure and the second determination procedure are repeated, and the predetermined An operation adjustment method for a soil heat source heat pump system, characterized in that an operation standard for a soil heat source heat pump system satisfying a temperature condition is obtained. An operation adjustment method of a soil heat source heat pump system combined with a secondary (load side) auxiliary heat source machine,
The soil heat source heat pump system operating heat load is an annual load,
The annual load amount is changed until the calculated value of the temperature on the heat source side satisfies the predetermined temperature condition, and the second simulation procedure and the second determination procedure are repeated, and the annual condition satisfying the predetermined temperature condition is satisfied. Based on the load amount, the first heat radiation amount integrated value for stopping the operation of the soil heat source heat pump system, which is the soil heat source heat pump system operation standard, or the soil heat source heat pump system and the secondary auxiliary heat source machine The operation adjustment method of the soil heat source heat pump system according to claim 3, wherein a second heat radiation amount integrated value for switching to the combined operation is obtained. An operation adjustment method of a soil heat source heat pump system combined with a primary side (heat source side) auxiliary heat source machine,
The soil heat source heat pump system operating heat load is an annual load,
Until the calculated value of the temperature on the heat source side satisfies the predetermined temperature condition, the temperature on the heat source side that operates the primary auxiliary heat source machine that is the soil heat source heat pump system operation standard (hereinafter referred to as a reference temperature). The method of adjusting the operation of the soil heat source heat pump system according to claim 3, wherein the reference temperature condition that satisfies the predetermined temperature condition is obtained by changing and repeating the second simulation procedure and the second determination procedure. . Heat and cold demand coexist and heat is shared between the heat exhaust heat pump's cold exhaust heat as a cooling operation heat pump heat source and the cooling operation heat pump's hot exhaust heat as a heat operation heat pump heat source through a common heat source water pipe Applying to the recovery system, in the case of a shortage of heat source, the operation adjustment method of the soil heat source heat pump system that uses the primary side auxiliary heat source machine together ,
One year is divided into a cooling period in which the cooling load is larger and a heating period in which the heating load is larger. In the cooling period, the cooling operation heat pump is connected to the soil heat source heat pump system, and the heating operation heat pump is cooled to the primary side (heat source Side) treated as an auxiliary heat source machine, in the heating period, the heating operation heat pump is treated as the soil heat source heat pump system, the cooling operation heat pump temperature exhaust heat is treated as a primary side auxiliary heat source machine,
The soil heat source heat pump system operating heat load is an annual load,
Until the calculated value of the temperature on the heat source side satisfies the predetermined temperature condition , the value related to the operation standard of the soil heat source heat pump system is changed and the second simulation procedure and the second determination procedure are repeated, The operation adjustment method of the soil heat source heat pump system according to claim 3, wherein an operation standard of the soil heat source heat pump system satisfying a predetermined temperature condition is obtained. It is applied to a heat recovery system that recovers exhaust heat through a common heat source water pipe, and is a method for adjusting the operation of a soil heat source heat pump system that uses a primary auxiliary heat source machine in combination when the heat source is insufficient ,
Treat the recovered exhaust heat as an auxiliary heat source,
The soil heat source heat pump system operating heat load is an annual load,
Until the calculated value of the temperature on the heat source side satisfies the predetermined temperature condition , the value related to the operation standard of the soil heat source heat pump system is changed and the second simulation procedure and the second determination procedure are repeated, The operation adjustment method of the soil heat source heat pump system according to claim 3, wherein an operation standard of the soil heat source heat pump system satisfying a predetermined temperature condition is obtained.   The predetermined temperature condition includes a condition that the calculated value of the temperature on the heat source side according to the second simulation procedure does not exceed the upper limit value and the lower limit value, or does not exceed the upper limit value or the lower limit value. The operation adjustment method of the soil heat source heat pump system according to any one of claims 3 to 7.   The predetermined temperature condition includes a condition that a secular change value in a calculated value of the maximum temperature and the minimum temperature on the heat source side according to the second simulation procedure does not exceed a predetermined condition value. The operation adjustment method of the soil heat source heat pump system of any one of 3 thru | or 7.   For each unit period, the soil heat source heat pump system operation standard is obtained by the ground heat characteristic analysis procedure, the resetting procedure, the second simulation procedure, and the second determination procedure, and the soil heat source heat pump system operation standard is obtained. The operation adjustment method of the soil heat source heat pump system according to any one of claims 3 to 9, wherein the operation adjustment of the soil heat source heat pump system is executed based on the method. A geothermal heat characteristic analysis device using an underground heat exchanger that circulates a heat medium ,
Assuming an effective thermal conductivity as the ground thermal characteristic value, a first time series is used to calculate a time-series change in temperature on the heat source side using a calculation condition measured every moment for a predetermined period using the effective conductivity. Simulation means of
The amount of change from the initial underground temperature in the predetermined period of the calculated value of the temperature on the heat source side by the first simulation means , and the initial underground temperature in the predetermined period of the measured value of the temperature on the heat source side And a first determination means for determining whether or not the amount of change from the first condition satisfies a predetermined condition,
The variation of the calculated value and the change amount of the measured value by changing the effective thermal conductivity to the predetermined condition is satisfied repeatedly determined by calculation and the first determining means according to the first simulation, An apparatus for analyzing ground thermal characteristics, wherein an effective thermal conductivity satisfying the predetermined condition is obtained. The temperature on the heat source side is the underground heat exchanger outlet temperature,
In the first simulation means, the ground heat exchanger inlet temperature and the circulating flow rate of the heat medium measured every moment during the predetermined period are given as calculation conditions, the heat balance inside the ground heat exchanger, infinite surroundings The ground thermal characteristic analysis apparatus according to claim 11, wherein heat conduction with the ground is analyzed, and a time-series change in the outlet temperature of the underground heat exchanger is calculated as the temperature on the heat source side. A ground thermal property analysis means for obtaining an effective thermal conductivity by the ground thermal property analysis method according to claim 1 or 2,
Resetting means for resetting the planned soil heat source heat pump system operating heat load, based on the integrated heat dissipation amount during the operation period;
Using the effective thermal conductivity by the geothermal heat characteristic analysis means and the soil heat source heat pump system operating heat load by the resetting means, a simulation of the operation of the soil heat source heat pump system is performed for the unit period after the present time, and the heat balance And a second simulation means for calculating a time-series change in temperature on the heat source side,
Second determination means for determining whether or not the calculated value of the temperature on the heat source side by the second simulation means satisfies a predetermined temperature condition;
Until the calculated value of the temperature on the heat source side satisfies the predetermined temperature condition, the value related to the soil heat source heat pump system operation standard is changed, and the calculation by the second simulation means and the determination by the second determination means are repeated. An operation adjustment device for a soil heat source heat pump system, wherein an operation standard for a soil heat source heat pump system that satisfies the predetermined temperature condition is obtained. A program for analyzing ground thermal characteristics using a ground heat exchanger that circulates a heat medium ,
Assuming an effective thermal conductivity as the ground thermal characteristic value, a first time series is used to calculate a time-series change in temperature on the heat source side using a calculation condition measured every moment for a predetermined period using the effective conductivity. Simulation process of
The amount of change from the initial underground temperature in the predetermined period of the calculated value of the temperature on the heat source side by the first simulation process , and the initial underground temperature in the predetermined period of the measured value of the temperature on the heat source side And a first determination process for determining whether or not a change amount from the first condition satisfies a predetermined condition,
The variation of the calculated value and the change amount of the measured value by changing the effective thermal conductivity to the predetermined condition is satisfied repeat the first simulation process and the first determination process, the predetermined condition A program characterized by obtaining an effective thermal conductivity satisfying The temperature on the heat source side is the underground heat exchanger outlet temperature,
In the first simulation process, the underground heat exchanger inlet temperature and the circulating flow rate of the heat medium measured every moment during the predetermined period are given as calculation conditions, and the heat balance inside the underground heat exchanger is infinite. 15. The program according to claim 14, wherein the heat conduction with the ground is analyzed, and the time series change of the outlet temperature of the underground heat exchanger is calculated as the temperature on the heat source side. A ground thermal property analysis process for obtaining an effective thermal conductivity by the ground thermal property analysis method according to claim 1 or 2,
A resetting process for resetting the planned soil heat source heat pump system operating heat load based on the integrated heat removal amount during the operation period;
Using the effective thermal conductivity by the geothermal heat characteristic analysis process and the soil heat source heat pump system operation heat load by the resetting process, a simulation of the operation of the soil heat source heat pump system is performed for the unit period after the current time, and the heat balance A second simulation process for calculating a time-series change in temperature on the heat source side,
Causing the computer to execute a second determination process for determining whether or not the calculated value of the temperature on the heat source side by the second simulation process satisfies a predetermined temperature condition;
Until the calculated value of the temperature on the heat source side satisfies the predetermined temperature condition, the value related to the soil heat source heat pump system operation standard is changed, and the second simulation process and the second determination process are repeated, A program characterized by obtaining an operating standard of a soil heat source heat pump system that satisfies a temperature condition.

Images