KR20150047657A - Sea water heat pump system using control of intaking sea water volume - Google Patents

Abstract

According to the present invention, a sea water heat source heat pump system using a control of a sea water intake volume can minimize a destruction of a marine environment which may be caused when discharging sea water since controlling the drain temperature of the sea water is possible by changing the intake volume of the sea water, entered into a sea water heat exchanger, in accordance with a difference between the intake temperature of the sea water, passing the sea water heat exchanger, and the drain temperature of the sea water.

Description

[0001] The present invention relates to a seawater heat pump system,

The present invention relates to a seawater heat source heat pump system, and more particularly, to a seawater heat source heat pump system capable of minimizing the influence on the surrounding environment by controlling the temperature difference between the intake and exhaust of seawater by controlling the intake amount of seawater.

Generally, fossil fuels such as coal, petroleum, and natural gas have been mainly used as the energy source for cooling and heating. However, fossil fuels have a problem of causing environmental pollution by discharging various pollutants in the combustion process. Therefore, alternative fuels that can replace fossil fuels are being actively developed. Alternative energy sources for cooling and heating include seawater, geothermal, and sewage heat.

Among alternative energy sources, the temperature change is very small, lower than the atmospheric temperature in summer and higher than the atmospheric temperature in winter, making it well suited for use as a heat source for heat pumps.

However, since the seawater absorbs or releases heat energy as it passes through the seawater heat exchanger, the temperature of the seawater drained into the sea after the heat exchange becomes higher or lower than the temperature of the seawater taken from the sea. There is a problem that when the difference between the drainage temperature of the seawater and the take-off temperature is excessively large, the sea environment can be destroyed due to the drainage of the seawater.

Patent Document 10-0690090 discloses a cascade heat pump system for seawater.

An object of the present invention is to provide a seawater heat source heat pump system using seawater withdrawal amount control that can minimize seawater destruction by regulating the drainage temperature of seawater.

A seawater heat source heat pump system using seawater intake water amount control according to the present invention comprises a seawater heat exchanger for absorbing heat or cold air of seawater, a heat pump for receiving heat or cool air absorbed by the seawater heat exchanger, And a control unit for controlling the operation of the seawater variable flow rate pump according to the temperature difference between the inlet and outlet sides of the seawater heat exchanger to control the flow rate of the seawater.

According to another aspect of the present invention, there is provided a seawater heat source heat pump system using seawater withdrawal amount control, comprising: a seawater heat exchanger for absorbing heat of the seawater or cool air; and a heat exchanger for exchanging heat between the water intake temperature of the seawater taken in the seawater heat exchanger and the seawater heat exchanger A seawater temperature sensor for measuring a drainage temperature of seawater drained into the sea; a seawater variable flow pump for controlling a flow rate of seawater taken in the seawater heat exchanger; a condenser for receiving hot or cool air absorbed in the seawater heat exchanger; A condenser temperature sensor for measuring an inlet and an outlet temperature of the condenser, an evaporator temperature sensor for measuring an inlet and an outlet temperature of the evaporator, and a heat exchanger for absorbing heat generated in the condenser during heating operation, A heat storage tank for absorbing cool air generated in the evaporator during cooling operation; Controlling the operation of the seawater variable flow rate pump according to the temperature difference between the inlet and outlet sides of the water heat exchanger to control the water intake flow rate of the seawater and circulating the condenser and the storage tank in accordance with the inlet and outlet temperature of the condenser during heating operation And a controller for controlling the flow rate of the cooling water for cooling the condenser and controlling the flow rate of the hot water circulating the evaporator and the seawater heat exchanger according to the inlet and outlet temperatures of the evaporator to provide heat to the evaporator.

A method of controlling a seawater heat source heat pump system according to the present invention includes the steps of: measuring a take-over temperature of seawater taken in a seawater heat exchanger and a drainage temperature of seawater discharged to the sea from the seawater heat exchanger; And increasing the flow rate of the seawater taken to the seawater heat exchanger when the difference in the drainage temperature is not less than a predetermined set value.

The seawater heat source heat pump system using the seawater withdrawal amount control according to the present invention can control the drainage temperature of the seawater by changing the withdrawal flow rate of the seawater flowing into the seawater heat exchanger according to the difference between the intake temperature and the drainage temperature of the seawater passing through the seawater heat exchanger, Which can minimize the destruction of the sea environment that can occur when the sea water is drained.

The supercooling degree of the refrigerant in the condenser or the overheating of the refrigerant in the evaporator can be prevented by changing the flow rate of the heat medium passing through the condenser or the evaporator according to the temperature difference between the inlet and outlet of the condenser or the evaporator. When the flow rate of the heating medium passing through the condenser or the evaporator is changed, the flow rate of the heating medium circulating in the sea water heat exchanger is changed and the heat exchange rate between the sea water and the heating medium is changed in the sea water heat exchanger. Thereby controlling the change in the drainage temperature of the seawater.

1 is a configuration diagram of a seawater heat source heat pump system according to an embodiment of the present invention.
FIG. 2 is a view showing an operation state of the seawater heat source heat pump system shown in FIG. 1 during a heating operation.
FIG. 3 is a view showing an operating state when the heating load of the seawater heat source heat pump system shown in FIG. 1 is small.
FIG. 4 is a view showing the operating state of the sea water heat source heat pump system shown in FIG. 1 during cooling operation.
5 is a schematic view showing a configuration for controlling the seawater variable flow pump shown in FIG.
FIG. 6 is a control block diagram of the seawater heat source heat pump system shown in FIG. 1; FIG.
FIG. 7 is a flowchart illustrating a method for controlling the amount of seawater intake during a heating operation of a seawater heat source heat pump system according to an embodiment of the present invention.
FIG. 8 is a flowchart illustrating a method for controlling the amount of seawater intake during the cooling operation of the seawater heat source heat pump system according to the embodiment of the present invention.

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

1 is a configuration diagram of a seawater heat source heat pump system according to an embodiment of the present invention.

1, the seawater heat source heat pump system includes a seawater storage 50, a seawater heat exchanger 20, a seawater flow controller, a heat pump 10, a main storage tank 80, an auxiliary storage tank 90, And includes a customer 100.

The seawater storage unit 50 is a seawater storage tank for temporarily storing seawater introduced from the sea. The seawater introduced from the sea is temporarily stored in the seawater storage unit 50 and then supplied to the seawater heat exchanger 20. The seawater storage unit 50 and the seawater heat exchanger 20 are connected to a seawater supply channel 21 to be described later. The present invention is not limited thereto, and it is of course possible that the seawater flows directly into the seawater heat exchanger 20 without passing through the seawater reservoir 50.

On the seawater supply passage 21, a filter 40 and a high-pressure cleaner 41 are installed.

The filter (40) is installed in at least one of the seawater supply passage (21) and the seawater reservoir (50) to filter seawater. For example, the filter 40 may be a filter or the like.

The high pressure washer 41 is integrally provided in the filter 40 or connected to the filter 40 to spray clean water to the filter 40 to clean the high pressure washer 41.

The seawater heat exchanger 20 absorbs heat or cold air of seawater and transfers the heat to the heat pump 10 through heat exchange. Since the temperature of the seawater is lower than the atmospheric temperature during the cooling operation of the heat pump 10 in summer, the cool air of the seawater is used in the heat pump 10. Since the temperature of the seawater is higher than the atmospheric temperature during the heating operation such as the winter season, the heat of the seawater can be used for the heat pump 10. The seawater heat exchanger 20 is connected to the evaporator 14 of the heat pump 10 and the first and second evaporator circulation passages 71 and 72 so that the heat absorbed by the seawater heat exchanger 20 Is transferred to the evaporator (14) through the first evaporator circulating passage (71). The seawater heat exchanger 20 is connected to the condenser 12 of the heat pump 10 and the first and second cooling passages 131 and 132 so that the cool air absorbed by the seawater heat exchanger 20 Is transmitted to the condenser (12) through the first cooling passage (131).

The seawater supply channel 21 and the seawater discharge channel 22 are connected to the seawater heat exchanger 20, respectively. A first seawater pump 1 for pumping and introducing seawater from the sea into the sea water supply passage 21; a second seawater pump 26 for pumping seawater stored in the seawater reservoir 50; A seawater flow meter 27 for measuring the flow rate of the seawater and a seawater supply valve 25 for interrupting the inflow of the seawater having passed through the filter 40 are installed.

The seawater supply passage 21 is provided with a seawater takeoff temperature sensor 23 for measuring the take-off temperature of the seawater taken in by the seawater heat exchanger 20.

The seawater discharge channel 22 is provided with a seawater drainage temperature sensor 24 for measuring the drainage temperature of the seawater drained into the sea after being heat-exchanged in the seawater heat exchanger 20.

The seawater flow rate control unit controls the flow rate of the seawater taken to the seawater heat exchanger 20, and a flow rate control valve or a flow rate control pump can be used. In the present embodiment, the seawater flow rate control unit is exemplified as the first seawater pump 1, but the present invention is not limited thereto, and the second seawater pump 2 may be used. In the first seawater pump 1, a variable-flow pump capable of varying the flow rate is used. The first seawater pump (1) is provided with an inverter drive unit (2).

The heat pump 10 includes a compressor 11, an evaporator 14, an expansion valve 13 and a condenser 12.

The evaporator (14) and the seawater heat exchanger (20) are connected to a second heat medium flow path through which the heat medium circulates. The second heat medium flow path is the first and second evaporator circulation flow paths 71 and 72. The first and second evaporator circulation conduits 71 and 72 pass heat medium absorbing heat from the seawater heat exchanger 20 and delivering the heat to the evaporator 14. The heating medium is a fluid such as water, and is absorbed by the seawater heat exchanger 20 to be transmitted.

A seawater heat exchanger flow rate controller and a flow meter 74 are installed in any one of the first and second evaporator circulation passages 71 and 72. The seawater heat exchanger flow rate control unit is a seawater heat exchanger variable flow rate pump 73 installed at the outlet side of the seawater heat exchanger 20 on the first evaporator circulation channel 71.

The evaporator 14 is connected to the main heat storage tank 80 and the auxiliary storage tank 90 through the third and fourth cooling passages 133 and 134. That is, since the cool air generated in the evaporator 14 is supplied to the main heat storage tank 80 and the auxiliary heat storage tank 90 during the cooling operation, the evaporator 14 is connected to the main storage tank 80 and the auxiliary storage tank 90 to the third and fourth cooling passages 133, 134. Therefore, the cooling heat medium, which has been heat-exchanged in the evaporator 14 during the cooling operation, flows into the evaporator 14 after passing through the main heat storage tank 80 and the auxiliary storage tank 90.

The third cooling air passage 133 is branched from the discharge side of the evaporator 14 on the second evaporator circulation passage 72 and connected to a first main storage tank flow path 81 to be described later.

The fourth cooling air passage 134 branches from the second auxiliary heat storage tank flow path 92 to be described later and joins to the inlet side of the evaporator 14 on the first evaporator circulation path 71.

The third three way valve 140 is installed at a position where the third cooling air passage 133 and the second evaporator circulating passage 72 are connected to each other and the third cooling air passage 133 and the first main heat accumulating tank passage 81 Way valve 141 is installed.

A twelfth three-way valve 142 is provided at a point where the fourth cooling air passage 134 and the first evaporator circulation passage 71 are connected to each other and the fourth cooling air passage 134 and the second auxiliary heat storage tank passage 92 And a thirteenth three-way valve 143 is installed at a point where the three-way valve 143 is connected. However, the present invention is not limited to this, and it is of course possible to switch the flow path of the heat pump 10 during the cooling and heating operations through a separate four-way valve (not shown) or the like.

An evaporator inlet temperature sensor 33 for sensing the temperature of the refrigerant flowing into the evaporator 14 is installed at the inlet side of the evaporator 14. An evaporator outlet temperature sensor 34 for sensing the temperature of the refrigerant discharged from the evaporator 14 is installed at the outlet of the evaporator 14.

The first and second condenser circulation conduits 15 and 16 are connected to the condenser 12. A heating medium for cooling the condenser 12 passes through the first and second condenser circulation passages 15 and 16. The heating medium may be a fluid such as water, or may be referred to as cooling water.

A second main storage tank flow path 82 and a second auxiliary storage tank flow path 92, which will be described later, are connected to the first condenser circulation flow path 15. A second three-way valve 62 is installed at a point where the first condenser circulation flow passage 15, the second main storage heat storage flow passage 82, and the second auxiliary heat storage flow passage 92 are connected.

The first main storage tank flow path 81 and the first auxiliary storage tank flow path 91 are connected to the second condenser circulation flow path 16. A first three-way valve (61) is installed at a point where the second condenser circulation flow passage (16) and the first main storage oil passage (81) are connected to the first auxiliary storage oil passage (91).

The condenser 12 is connected to the seawater heat exchanger 20 by the first and second cooling passages 131 and 132. That is, since the cool air absorbed in the seawater heat exchanger 20 during cooling operation must be used to cool the condenser 12, the condenser 12 is connected to the seawater heat exchanger 20, (131) (132). Accordingly, the heating medium, which absorbs the cold air in the seawater heat exchanger 20 during the cooling operation, flows into the condenser 12 through the first cooling flow path 131, is heat-exchanged in the condenser 12, And circulates to the seawater heat exchanger (20) through the cooling channel (132).

The first cooling air flow path 131 is branched from the first evaporator circulation path 71 and merged to the inlet side of the condenser 12.

The second cooling air flow path 132 branches from the discharge side of the condenser 12 and joins to the inlet side of the seawater heat exchanger 20 on the second evaporator circulation flow path 72.

A seventh three-way valve 137 is installed at a point where the first cooling air passage 131 and the first evaporator circulation passage 71 are connected.

An eighth three-way valve 138 is installed at a position where the second cooling air passage 132 and the second evaporator circulation passage 72 are connected.

And a ninth three-way valve 138 is installed at a position where the second cooling passage 132 and the second condenser circulation passage 16 are connected to each other.

A condenser inlet temperature sensor 31 for sensing the temperature of the refrigerant flowing into the condenser 12 is installed at the inlet side of the condenser 12. A condenser outlet temperature sensor 32 for sensing the temperature of the refrigerant discharged from the condenser 12 is installed at the outlet of the condenser 12.

The main heat storage tank 80 absorbs at least a part of the heat or cool air generated by the heat pump 10 and transfers the heat to the heat consumer 100. That is, the heat generated by the condenser 12 of the heat pump 10 is absorbed and stored during the heating operation of the heat pump 10, and is generated by the evaporator 14 of the heat pump 10 during the cooling operation. Absorbs the cold air and stores it. A buffer tank may be used as the main heat storage tank 80, and any buffer tank may be used as long as it can transfer heat or cool air absorbed by the heat pump 10 to the heat consumer 100.

The first and second main storage tank passages 81 and 82 are connected to the main storage tank 80. The first and second main storage tank passages 81 and 82 are connected to the first and second condenser circulation passages 15, (16). The first and second three-way valves 61 and 62 are installed at the points where the first and second main storage tank flow paths 81 and 82 are connected to the first and second condenser circulation flow paths 15 and 16, respectively. The first and second three-way valves 61 and 62 are also connected to the first and second storage tank flow paths 91 and 92 described later. The main heat storage tank 80 is connected to the heat consumers 100 through the third and fourth main heat storage tanks 83 and 84.

The first main storage tank flow path 81 is provided with a storage tank flow rate control unit for controlling the flow rate of the heating medium flowing into the main storage tank 80. The storage tank flow rate control unit is a storage tank variable flow rate pump 85 provided at the inlet side of the main storage tank 80. The variable flow rate pump 85 is controlled in operation by a control section described later. In the present embodiment, a variable flow rate pump is provided only at the inlet side of the main storage tank 80, but it is also possible to provide a variable flow rate pump at the inlet side of the auxiliary storage tank 80 .

The auxiliary heat storage tank 90 is a heat storage tank for storing the remaining heat or cool air absorbed by the heat pump 10 other than that absorbed by the main heat storage tank 80. That is, the heat generated by the condenser 12 of the heat pump 10 is absorbed and stored during the heating operation of the heat pump 10, and is generated by the evaporator 14 of the heat pump 10 during the cooling operation. Absorbs the cold air and stores it.

The first and second storage tank passages 91 and 92 are connected to the auxiliary storage tank 90. The first and second auxiliary storage tank passages 91 and 92 are connected to the first and second three way valves 61 and 62 . A flow meter 95 is installed in the first and second auxiliary storage tank passages 91 and 92. In addition, the auxiliary storage tank 90 is connected to the heat consumer 100 through the third and fourth storage tank passages 93 and 94.

A plurality of the heat demanders 100 may be provided. In the present embodiment, the first and second heat demanders 101 and 102 are provided. The first, second, third, and fourth heat source flow channels 111, 112, 113, and 114 are connected to the first and second heat demanders 101 and 102. The third main storage tank flow path 83 and the fourth storage tank flow path 94 are merged into the fifth heat demand source flow path 115 and a third three way valve 63 is installed at the merging point. A fourth three-way valve (64) is installed at a point where the fifth heat demand channel (115) branches to the first and second heat demand channel (111, 112). A fifth five-way valve 65 is provided at a point where the third and fourth heat demand channel 113 and 114 are joined and the third and fourth heat demand channel 113 and 114 are connected to the sixth heat demand channel, (116). A sixth three-way valve 66 is installed at a point where the sixth heat demand channel 116 branches to the fourth main tank passage 84 and the third storage tank channel 83.

The fifth heat demand channel 115 is provided with a heat demand source pump 117 for controlling the flow rate supplied to the heat demander 100.

The heat pump system further includes a control unit 200 for controlling the operation of the first seawater pump 1 according to the temperature difference sensed by the seawater intake water temperature sensor 23 and the seawater drainage temperature sensor 24, respectively do. The control unit 200 also controls the operation of the regenerator variable flow rate pump 83 in accordance with the temperature difference sensed by the condenser inlet temperature sensor 31 and the condenser outlet temperature sensor 32 during the heating operation. The control unit 200 also controls the operation of the seawater heat exchanger variable flow rate pump 84 in accordance with the temperature difference sensed by the evaporator inlet temperature sensor 33 and the evaporator outlet temperature sensor 34 during the heating operation . The control unit 200 also controls the operation of the storage tank variable flow rate pump 83 according to the temperature difference detected by the evaporator inlet temperature sensor 33 and the evaporator outlet temperature sensor 34 during the cooling operation. The control unit 200 also controls the operation of the seawater heat exchanger variable flow rate pump 84 in accordance with the temperature difference sensed by the condenser inlet temperature sensor 31 and the condenser outlet temperature sensor 32 during the heating operation .

The operation of the heat pump system according to the present invention will now be described.

First, the heating operation of the heat pump system will be described with reference to Figs. 2 and 3. Fig.

The seawater is passed through the seawater storage unit 50, the filter 40, and the seawater heat exchanger 20 in order, and then discharged to the sea.

In the seawater heat exchanger 20, heat exchange is performed between the seawater and the heat medium circulating through the first and second evaporator circulation passages 71 and 72. The heat medium absorbing the heat of the sea water transfers heat to the evaporator 14.

The heat transferred to the evaporator 14 is transferred to the refrigerant circulating through the heat pump 10 and transferred to the heat medium passing through the second condenser circulation passage 16 through heat exchange in the condenser 10 .

At least a part of the heat medium that has absorbed heat while passing through the condenser 10 flows into the main heat storage tank 80 and the rest is introduced into the auxiliary storage tank 90.

The heat absorbed by the main storage tank 80 is supplied to the heat consumer 100, and the heat absorbed by the auxiliary storage tank 90 is temporarily stored. At this time, it is also possible that the heat of the auxiliary heat storage tank 90 is supplied to the heat consumer 100 together. In the present embodiment, it is assumed that the heating load is small or the heat of the auxiliary heat storage tank 90 is supplied to the heat consumer 100 when the heat pump 10 is not operated.

3, a description will be given of a case where the heating load of the heat demander 100 is less than the set load or there is a heating load of the heat pump 10 or the maintenance of the seawater heat exchanger 20. FIG.

The operation of the seawater pump 1 is stopped and no operation of the heat pump 10 and the main heat storage tank 80 is stopped.

At this time, the heat stored in the auxiliary storage tank (90) can be supplied to the heat consumer (100). That is, the third three-way valve 63 interrupts the third main storage tank passage 83, opens the fourth storage tank passage 94, and the heating water stored in the auxiliary storage tank 90 is supplied to the heat consumer 100).

The heating water used in the heat consumer 100 is discharged to the auxiliary storage tank 90 through the sixth three-way valve 66 again.

The heat pump system according to the present invention is characterized in that the heat generated by the heat pump 10 is distributed to the main storage tank 80 and the auxiliary storage tank 90 so that the heat pump 10 and the seawater heat exchange It is possible to supply the heat source to the heat consumer 100 at the same time when the machine 20 is not operated.

4, the cooling operation of the heat pump system according to the present invention will be described.

When the cooling is required in summer, since the temperature of the seawater is lower than the temperature of the atmosphere, it can be supplied to the heat consumer using the cold air of the seawater.

The seawater heat exchanger 20 exchanges heat between the seawater and the heat medium. At this time, since the temperature of the seawater is low, the heat medium absorbs the cold air of the seawater.

The heat medium, which has absorbed cold air of seawater through heat exchange in the seawater heat exchanger 20, flows into the condenser 12 through the first cooling flow path 131.

The heating medium flowing into the condenser 12 is circulated to the seawater heat exchanger 20 through the second cooling flow path 132 after cooling the condenser 12.

In the evaporator 14, heat exchange is performed between the main heat storage tank 80 and the heating medium supplied from the auxiliary storage tank 90 and the refrigerant. The heat medium that has been heat-exchanged and cooled in the evaporator 14 flows into the main heat storage tank 80 and the auxiliary storage tank 90 through the third cooling air flow path 133. Therefore, cool air can be stored in the main storage tank 80 and the auxiliary storage tank 90.

The cool air stored in the main heat storage tank 80 and the auxiliary storage tank 90 can be selectively supplied to the heat consumer 100 according to the load of the heat consumer 100. That is, as in the case of the heating operation, when the cooling load of the heat consumer 100 is equal to or higher than the set load, the cooling heat of the main heat storage tank 80 is supplied. If the cooling load of the heat consumer 100 is less than the set load, The coolant of the auxiliary heat storage tank 90 can be supplied to the heat consumer 100 at the same time that the pump 10 is not operated.

As described above, when the heating operation is performed, the heat consumer can be heated using the heat of the seawater, and when the cooling operation is performed, the heat consumer can be cooled using the cold air of the seawater.

Hereinafter, a control method of the seawater heat source heat pump system according to the present invention will be described.

First, a control method in heating operation will be described with reference to Figs. 5 and 6. Fig.

The take-off temperature and the drainage temperature of the seawater are measured from the seawater take-off temperature sensor (23) and the seawater drainage temperature sensor (24). Further, the inlet temperature and the outlet temperature of the condenser 12 are measured from the condenser inlet temperature sensor 31 and the condenser outlet temperature sensor 32. Also, the inlet temperature and the outlet temperature of the evaporator 14 are measured from the evaporator inlet temperature sensor 33 and the evaporator outlet temperature sensor 34. (S10)

The control unit 200 determines whether the difference between the water intake temperature and the water drainage temperature of the seawater is equal to or greater than a predetermined set value. (S11)

When the temperature of the cooled seawater under heat exchange in the seawater heat exchanger 20 is excessively low, the difference between the take-in temperature and the drainage temperature of the seawater becomes equal to or greater than the set value. If sea water is excessively lowered and drained into the sea, the environment of the sea may be destroyed. The control unit 200 controls the operation of the first seawater pump 1 to increase the water intake flow rate of seawater flowing in from the sea (S12) (S13)

When the water intake flow rate of the seawater is increased, the flow rate of the seawater passing through the seawater heat exchanger 20 is increased and the temperature change of the seawater passing through the seawater heat exchanger 20 is reduced. Therefore, since the drainage temperature of the seawater is increased, it is possible to minimize the destruction of the marine environment by the drainage of the seawater.

Also, the controller 200 compares the difference between the inlet temperature and the outlet temperature of the condenser 12 with a predetermined set value (S14)

If the difference between the inlet temperature and the outlet temperature of the condenser 12 is equal to or greater than the preset value, the refrigerant passing through the condenser 12 is in a supercooled state. Accordingly, the operation of the heat storage tank variable flow rate pump 85 is controlled to reduce the flow rate of the heat medium that cools the condenser 12. When the flow rate of the heat medium flowing into the condenser 12 is reduced, the difference between the inlet temperature and the outlet temperature of the condenser 12 can be reduced. (S15) (S26)

Also, the controller 200 compares the difference between the inlet temperature and the outlet temperature of the evaporator 14 with a predetermined set value (S17)

If the difference between the inlet temperature and the outlet temperature of the evaporator 14 is equal to or greater than the set value, the operation of the seawater heat exchanger variable flow rate pump 73 is controlled to reduce the flow rate of the heat medium supplied to the evaporator 14 . When the flow rate of the heat medium flowing into the evaporator 14 is reduced, the difference between the inlet temperature and the outlet temperature of the condenser 12 can be reduced. (S18) (S19)

When the temperature change of the heating medium passing through the evaporator 14 is reduced, the heat exchange rate in the seawater heat exchanger 20 is reduced. If the heat exchange rate in the seawater heat exchanger 20 is reduced, the difference between the water intake temperature and the water drain temperature of the seawater passing through the seawater heat exchanger 20 can also be reduced. Therefore, it is possible to minimize the destruction of the sea environment due to the difference between the water intake temperature and the water discharge temperature of the seawater.

Referring to Fig. 8, a control method in cooling operation will be described.

The take-off temperature and the drainage temperature of the seawater are measured from the seawater take-off temperature sensor (23) and the seawater drainage temperature sensor (24). Further, the inlet temperature and the outlet temperature of the condenser 12 are measured from the condenser inlet temperature sensor 31 and the condenser outlet temperature sensor 32. Also, the inlet temperature and the outlet temperature of the evaporator 14 are measured from the evaporator inlet temperature sensor 33 and the evaporator outlet temperature sensor 34. (S20)

The control unit 200 determines whether the difference between the water intake temperature and the water drainage temperature of the seawater is equal to or greater than a predetermined set value. (S21)

Since the temperature of the seawater is low during the cooling operation, the seawater in the seawater heat exchanger 20 transfers the cool air while absorbing heat while exchanging heat. When the temperature of the heated seawater is excessively high during heat exchange in the seawater heat exchanger 20, the difference between the intake temperature and the drain temperature of the seawater becomes equal to or greater than a set value. If the sea water is drained to sea by high temperature sea water whose temperature is excessively high, the sea environment may be destroyed. The control unit 200 controls the operation of the first seawater pump 1 to increase the flow rate of the seawater flowing in from the sea (S22) (S23)

When the water intake flow rate of the seawater is increased, the flow rate of the seawater passing through the seawater heat exchanger 20 is increased and the temperature change of the seawater passing through the seawater heat exchanger 20 is reduced. Therefore, since the drainage temperature of the seawater is lowered, it is possible to minimize the destruction of the sea environment by the drainage of the seawater.

Also, the controller 200 compares the difference between the inlet temperature and the outlet temperature of the condenser 12 with a predetermined set value (S24)

If the difference between the inlet temperature and the outlet temperature of the condenser 12 is equal to or greater than the preset value, the refrigerant passing through the condenser 12 is in a supercooled state. The heat medium for cooling the condenser 12 flows through the seawater heat exchanger 20 during the cooling operation so that the operation of the seawater heat exchanger variable flow rate pump 73 is controlled so that the heat medium for cooling the condenser 12 . When the flow rate of the heat medium flowing into the condenser 12 is reduced, the difference between the inlet temperature and the outlet temperature of the condenser 12 can be reduced. (S25) (S26)

When the temperature change of the heating medium passing through the condenser 12 is reduced, the heat exchange rate in the seawater heat exchanger 20 is reduced. If the heat exchange rate in the seawater heat exchanger 20 is reduced, the difference between the water intake temperature and the water drain temperature of the seawater passing through the seawater heat exchanger 20 can also be reduced. Therefore, it is possible to minimize the destruction of the sea environment due to the difference between the water intake temperature and the water discharge temperature of the seawater.

Also, the controller 200 compares the difference between the inlet temperature and the outlet temperature of the evaporator 14 with a predetermined set value (S27)

If the difference between the inlet temperature and the outlet temperature of the evaporator 14 is equal to or greater than a set value, the operation of the heat storage tank variable flow rate pump 85 is controlled to reduce the flow rate of the heat medium supplied to the evaporator 14. When the flow rate of the heat medium flowing into the evaporator 14 is reduced, the difference between the inlet temperature and the outlet temperature of the condenser 12 can be reduced. (S28) (S29)

As described above, it is possible to adjust the drainage temperature of the seawater by changing the withdrawal flow rate flowing into the seawater heat exchanger 20 according to the difference between the take-over temperature and the drainage temperature of the seawater passing through the seawater heat exchanger 20, It is possible to minimize the destruction of the marine environment that may occur in the drainage of water.

The supercooling degree of the refrigerant in the condenser or the overheating of the refrigerant in the evaporator can be prevented by changing the flow rate of the heat medium passing through the condenser or the evaporator according to the temperature difference between the inlet and outlet of the condenser or the evaporator. When the flow rate of the heating medium passing through the condenser or the evaporator is changed, the flow rate of the heating medium circulating in the sea water heat exchanger is changed and the heat exchange rate between the sea water and the heating medium is changed in the sea water heat exchanger. Thereby controlling the change in the drainage temperature of the seawater.

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.

1: First seawater pump 10: Heat pump
12: condenser 14: evaporator
20: Sea water heat exchanger 23: Sea water intake temperature sensor
24: seawater drainage temperature sensor 31: condenser inlet temperature sensor
32: condenser outlet temperature sensor 33: evaporator inlet temperature sensor
34: evaporator outlet temperature sensor 73: seawater heat exchanger variable flow pump
80: main heat storage tank 90: auxiliary storage tank
85: regenerative tank variable flow pump 200:

Claims (17)

A seawater heat exchanger for absorbing the heat of the seawater or the cold air;
A heat pump which receives heat or cool air absorbed by the seawater heat exchanger;
A seawater flow rate controller for controlling the flow rate of the seawater taken to the seawater heat exchanger;
And a control unit controlling the operation of the seawater variable flow rate pump according to the temperature difference between the inlet and outlet sides of the seawater heat exchanger to control the water intake flow rate of the seawater. The method according to claim 1,
A seawater intake water temperature sensor for measuring a water intake temperature of the seawater taken in the seawater heat exchanger;
Further comprising a seawater drainage temperature sensor for measuring a drainage temperature of the seawater drained into the sea after heat exchange in the seawater heat exchanger,
Wherein the control unit controls the operation of the seawater flow rate control unit according to a difference between the sensed temperatures of the seawater intake temperature sensor and the seawater drainage temperature sensor. The method according to claim 1,
A condenser provided in the heat pump and condensing the refrigerant,
A heat storage tank for absorbing and storing heat in the condenser during heating operation of the heat pump,
Further comprising a heat storage tank flow rate control unit installed on a flow path connecting the condenser and the storage tank and controlling a flow rate of a heating medium flowing from the condenser to the storage tank,
Wherein the control unit controls the operation of the thermal storage tank flow rate control unit in accordance with the temperature difference between the inlet and outlet sides of the condenser during heating operation. The method of claim 3,
Further comprising a seawater heat exchanger flow rate control unit installed on the flow path connecting the seawater heat exchanger and the condenser during cooling operation of the heat pump and controlling the flow rate of the heat medium flowing into the condenser in the seawater heat exchanger,
Wherein the control unit controls the operation of the seawater heat exchanger flow rate control unit in accordance with the temperature difference between the inlet and outlet sides of the condenser during cooling operation. The method of claim 4,
A condenser inlet temperature sensor for measuring the inlet temperature of the condenser,
Further comprising a condenser outlet temperature sensor for measuring an outlet temperature of the condenser,
Wherein the control unit controls the operation of the thermal storage tank flow rate control unit and the seawater heat exchanger flow rate control unit according to the difference between the condenser inlet temperature sensor and the condenser outlet temperature sensor. The method according to claim 1,
An evaporator provided in the heat pump,
Further comprising a seawater heat exchanger flow rate control unit installed on the flow path connecting the seawater heat exchanger and the evaporator and controlling the flow rate of the heat medium flowing into the evaporator from the seawater heat exchanger,
Wherein the control unit controls the operation of the seawater heat exchanger flow rate control unit according to a temperature difference between an inlet side and an outlet side of the evaporator during a heating operation. The method of claim 6,
A heat storage tank for absorbing and storing cold air in the evaporator during cooling operation of the heat pump,
Further comprising a heat storage tank flow rate control unit installed on a flow path connecting the evaporator and the storage tank to control a flow rate of a heating medium flowing from the evaporator to the storage tank,
Wherein the control unit controls the operation of the thermal storage tank flow control unit according to the temperature difference between the inlet and outlet sides of the evaporator during cooling operation. The method of claim 7,
An evaporator inlet temperature sensor for sensing an inlet temperature of the evaporator,
Further comprising an evaporator outlet temperature sensor for sensing an outlet temperature of the evaporator,
Wherein the control unit controls the operation of the thermal storage tank flow rate control unit and the seawater heat exchanger flow rate control unit in accordance with the difference between the evaporator inlet temperature sensor and the evaporator outlet temperature sensor. The method according to any one of claims 1 to 8,
Wherein the seawater flow rate control unit includes a seawater variable flow rate pump installed in a seawater supply channel for supplying seawater to the seawater heat exchanger. The method according to claim 3 or 7,
Wherein the thermal storage tank flow rate control unit includes a variable flow rate pump installed at an inlet side of the thermal storage tank. The method according to claim 4 or 6,
The seawater heat exchanger flow rate control unit includes a variable flow rate pump installed at an inlet side of the evaporator. The method of claim 3,
The heat storage tank,
A main heat storage tank for absorbing and storing heat or cool air generated from the heat pump;
And an auxiliary heat storage tank for absorbing and storing the remaining heat or cool air generated by the heat pump,
Wherein the control unit controls the seawater intake amount control to control the heat of at least one of the main storage tank and the auxiliary storage tank to be supplied to the heat consumer according to the load of the heat pump. A seawater heat exchanger for absorbing the heat of the seawater or the cold air;
A seawater temperature sensor for measuring a take-over temperature of the seawater taken in the seawater heat exchanger and a drainage temperature of the seawater drained into the sea after being heat-exchanged in the seawater heat exchanger;
A seawater variable flow pump for controlling the flow rate of the seawater taken to the seawater heat exchanger;
A heat pump including a condenser and an evaporator that receive the hot or cool air absorbed by the seawater heat exchanger;
A condenser temperature sensor for measuring an inlet and an outlet temperature of the condenser;
An evaporator temperature sensor for measuring an inlet and an outlet temperature of the evaporator;
A heat storage tank for absorbing heat generated in the condenser during heating operation and absorbing cold air generated in the evaporator during cooling operation;
The control unit controls the operation of the seawater variable flow rate pump in accordance with the temperature difference between the inlet and outlet sides of the seawater heat exchanger during cooling and heating operations to control the water intake flow rate of the seawater, And a control unit for controlling the flow rate of the cooling water for cooling the condenser while circulating the condenser and controlling the flow rate of the hot water circulating the evaporator and the seawater heat exchanger in accordance with the inlet and outlet temperatures of the evaporator, A seawater heat source heat pump system comprising a control unit. 14. The method of claim 13,
Wherein the control unit controls the flow rate of cooling water for circulating the condenser and the seawater heat exchanger according to the inlet and outlet temperatures of the condenser during cooling operation to cool the condenser, And a control unit for controlling a flow rate of hot water circulating through the thermal storage tank and providing heat to the evaporator. Measuring a take-off temperature of the seawater taken in the seawater heat exchanger and a drainage temperature of the seawater drained into the sea from the seawater heat exchanger;
And increasing the flow rate of the seawater to be taken into the seawater heat exchanger when the difference between the take-in temperature of the seawater and the drainage temperature is equal to or greater than a predetermined set value. 16. The method of claim 15,
Measuring an inlet temperature and an outlet temperature of the condenser of the heat pump, respectively,
Further comprising increasing the flow rate of cooling water circulating through the condenser if the difference between the inlet temperature and the outlet temperature of the condenser is greater than a predetermined set value. 16. The method of claim 15,
Measuring an inlet temperature and an outlet temperature of the evaporator of the heat pump, respectively,
Further comprising the step of increasing the flow rate of the hot water circulating through the evaporator if the difference between the inlet temperature and the outlet temperature of the evaporator is equal to or greater than a predetermined set value.

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