Energy System using Simple Thermal Storage Tank

Abstract

The energy system of the present invention comprises a heat source circulation unit, a plurality of heat load circulation units in which each heat load independently forms a circulation system and can be selectively operated, and a heat relay circulation unit that thermally connects the plurality of heat load circulation units in parallel to the heat source circulation unit to exchange heat energy in common among the plurality of heat load circulation units. The heat relay circulation unit comprises a heat storage unit for storing at least one of the residual heat source and waste heat recovered from the plurality of heat load circulation units. The control unit controls the system so that, in a normal operation mode, the heat energy recovered by the heat storage unit is stored, and in a special operation mode, the heat energy stored by the heat storage unit is used to enable heat exchange among the plurality of heat load circulation units in common.

Description

Technology Field

[0001] The present invention relates to an energy system using a heat storage unit, and more specifically, to an energy system capable of improving performance and efficiency by storing waste heat and residual heat sources in a simple heat storage tank and utilizing them as a heat source for heating and cooling a building. Background Technology

[0002] Recently, to reduce carbon emissions, heat pump-type energy systems utilizing geothermal or air heat are being developed for public buildings as alternatives to conventional fossil fuels.

[0003] Among these, the geothermal energy system utilizes underground heat sources that can be consistently used for heating and cooling regardless of climate conditions or seasonal changes. It is a system that uses groundwater located at a certain depth or greater, which possesses the heat source, as the energy for heating and cooling a building through heat exchange between the ground and a highly energy-efficient heat pump.

[0004] An air source energy system is a system that absorbs heat from low-temperature air through the compression and expansion process of a refrigerant and transfers it to the indoors (heating) or releases the heat from the indoors to the outside (cooling). Since it utilizes infinite heat from the atmosphere, it can produce 3 to 4 times more thermal energy than the input electrical energy, making it a highly efficient energy system.

[0005] In geothermal energy systems, the condition of the required heat source is critical. If the heat source exceeds the required level (during cooling) or falls below it (during heating), it is not utilized as a cooling or heating source but remains as residual heat. As a result, this residual heat is mixed with newly acquired geothermal heat from the underground heat exchanger, leading to the use of unnecessary power to acquire that unnecessary geothermal heat or its waste.

[0006] Meanwhile, the efficiency of air source energy systems drops significantly when the outdoor temperature falls sharply, as the amount of heat that can be absorbed from the heat source decreases. Additionally, frost formation occurs on the surface of the outdoor unit coil during winter, causing heating to be temporarily suspended and consuming additional energy during the defrosting operation to remove the frost.

[0007] Furthermore, as the temperature difference between the indoor and outdoor environments increases, the compressor in the heat pump system must work harder; consequently, power consumption increases and output decreases, causing the coefficient of performance to drop sharply. In particular, when outdoor temperatures drop below freezing in winter, the lack of heat sources in the air may prevent the system from meeting the set indoor temperature. Consequently, the compressor rotates at high speeds for extended periods, leading to accumulated mechanical stress and a shortened lifespan. Prior art literature

[0008] Registered Patent No. 10-1184699 Registered Patent No. 10-2760795 Registered Patent No. 10-1043031 The problem to be solved

[0009] To solve the aforementioned problems, the objective of the present invention is to provide an energy system capable of storing residual heat or waste heat in a heat storage unit and supplying a heating and cooling heat source without or with minimal underground heat exchange during the initial preheating function of the system operation, as well as during periods of severe load fluctuations such as transitional seasons and small loads.

[0010] Another objective of the present invention is to provide an energy system capable of providing uninterrupted heating to the indoors by utilizing the residual heat of the thermal storage tank, even when the heat pump stops heating for defrosting.

[0011] Another objective of the present invention is to provide an energy system capable of utilizing waste heat by cooling a thermal storage tank with discarded condensate.

[0012] However, the technical problems that this embodiment aims to solve are not limited to the technical problems described above, and other technical problems may exist. means of solving the problem

[0013] The energy system of the present invention for achieving the above objective comprises a heat source circulation unit, a plurality of heat load circulation units in which each heat load independently forms a circulation system and can be selectively operated, and a heat relay circulation unit that thermally connects the plurality of heat load circulation units in parallel to the heat source circulation unit to exchange heat energy in common among the plurality of heat load circulation units. The heat relay circulation unit comprises a heat storage unit for storing at least one of the residual heat source and waste heat recovered from the plurality of heat load circulation units. The control unit stores the heat energy recovered in the heat storage unit in a normal operation mode, and controls the plurality of heat load circulation units to exchange heat in common using the heat energy stored in the heat storage unit in a special operation mode.

[0014] In the present invention, the heat storage unit is composed of at least one vertically elongated simple heat storage tank, and each simple heat storage tank is divided into an upper layer and a lower layer by a separating partition, and the lower layer is used as a buffer layer, and the matured heat stored water in the upper layer can be connected to a connecting pipe in a bypass manner.

[0015] In the present invention, the simple thermal storage tank is preferably supplied with condensate through a coil pipe extending spirally from the lower layer to the upper layer, and the condensate is preferably supplied from a condensate insulation tank.

[0016] In the present invention, it is preferable that the simple thermal storage tank further incorporates a temperature controller capable of controlling the temperature of the thermal storage water discharged at the upper outlet side.

[0017] In the present invention, the heat source circulation unit may be either geothermal heat or air heat. Effects of the invention

[0018] As described above, the energy system of the present invention utilizes a simplified thermal storage tank to store residual heat and waste heat generated within the system. This enables the supply of heating and cooling heat without or with minimal exchange with heat sources, such as ground heat or air heat, during the initial preheating phase of system operation or during periods of significant load fluctuation, such as transitional seasons or small-scale load swings. Consequently, the system can be operated with minimal power, thereby increasing the coefficient of performance. Furthermore, condensate generated during system operation can be transferred to a condensate insulation tank separate from the simplified thermal storage tank and utilized for cold water storage during heating and cooling, allowing for the reuse of the condensate. Additionally, the simplified thermal storage tank features a modular structure that allows for expansion or reduction as needed, making replacement and maintenance easy.

[0019] However, the effects of the present invention are not limited to those mentioned above, and other effects not mentioned above will be clearly understood by those skilled in the art within the scope and spirit of the present invention. Brief explanation of the drawing

[0020] FIG. 1 is a circulation diagram of a preferred embodiment of an energy system using a heat storage unit according to the present invention. FIG. 2 is a drawing illustrating a preferred embodiment of a simple thermal storage tank according to the present invention. FIG. 3 is a circulation diagram of a preferred embodiment of a geothermal energy system using a simple thermal storage tank according to the present invention. Figure 4 is a table showing data measured for 10 hours in January using the energy system of Figure 3. Figure 5 is a table showing data measured for 10 hours in August using the energy system of Figure 3. FIG. 6 is a circulation diagram of a preferred embodiment of an air heat energy system using a simple thermal storage tank according to the present invention. Specific details for implementing the invention

[0021] With respect to the embodiments of the present invention disclosed in the text, specific structural or functional descriptions are provided merely for the purpose of explaining the embodiments of the present invention, and the embodiments of the present invention may be implemented in various forms and should not be interpreted as being limited to the embodiments described in the text.

[0022] The present invention is susceptible to various modifications and may take various forms, and specific embodiments are illustrated in the drawings and described in the text. However, this is not intended to limit the invention to the specific disclosed forms, and it should be understood that the invention includes all modifications, equivalents, and substitutions that fall within the spirit and scope of the invention. Similar reference numerals have been used for components in the description of each drawing.

[0023] The terms used in this application are used merely to describe specific embodiments and are not intended to limit the invention. The singular expression includes the plural expression unless the context clearly indicates otherwise.

[0024] Unless otherwise defined, all terms used herein, including technical or scientific terms, have the same meaning as generally understood by those skilled in the art to which the present invention pertains. Terms such as those defined in commonly used dictionaries should be interpreted as having a meaning consistent with their meaning in the context of the relevant technology, and should not be interpreted in an ideal or overly formal sense unless explicitly defined in this application.

[0025] Hereinafter, the best mode for carrying out the present invention will be described in more detail with reference to the attached drawings. Identical components in the drawings are given the same reference numerals, and redundant descriptions of identical components are omitted.

[0026] FIG. 1 is a circulation diagram of a preferred embodiment of an energy system using a heat storage unit according to the present invention.

[0027] Referring to the drawing, the energy system (1) comprises a heat source circulation unit (10), a plurality of heat load circulation units (30; 32, 34, 36) in which each heat load independently forms a circulation system and can be selectively operated, and a heat relay circulation unit (20) that heat-couples the plurality of heat load circulation units (30) in parallel to the heat source circulation unit (10) to exchange heat energy in common among the plurality of heat load circulation units (30).

[0028] The heat source circulation unit (10) may be a ground heat circulation unit utilizing ground heat or an outdoor unit utilizing outdoor air heat. A plurality of heat load circulation units (30) can be operated independently of each other and selectively operated with heat pumps corresponding to each energy load space. The heat relay circulation unit (20) connects a plurality of heat load circulation units (30) in parallel and relays the heat energy of the heat source circulation unit. The heat relay circulation unit (20) further includes a heat storage unit (40) for storing at least one of the residual heat source and waste heat recovered from the plurality of heat load circulation units (30). In normal operation mode, the control unit (50) controls the circulation pump of the heat source circulation unit (10) and the circulation pump of the heat relay circulation unit (20) to exchange heat and store the heat energy recovered in the heat storage unit (40). In the special operation mode, the control unit (50) stops the circulation pump of the heat source circulation unit (10) and controls the circulation pump of the heat relay circulation unit (20) so that the heat energy stored in the heat storage unit (40) is used to control the multiple heat load circulation units (30) to exchange heat in common.

[0029] FIG. 2 is a drawing illustrating a preferred embodiment of a simple thermal storage tank according to the present invention.

[0030] Referring to FIG. 2, the simple thermal storage tank (100) includes a vertically elongated rectangular cylindrical tank (110), a condensate insulation tank (120), and a temperature controller (130) for adultification.

[0031] The internal space of the tank (110) is separated into upper and lower layers (114, 116) through an intermediate heat exchange separation partition (112). The upper layer (114) is connected by a bypass to the primary side connection pipe and recovery pipe of the heat pump through the inlet / outlet (115). Therefore, during the process of recovery after heat exchange, the residual heat source is stored in the upper layer (114) of the heat storage tank. The upper layer (114) is configured so that the outlet (OUT) is located higher than the inlet (IN), thereby allowing stratified, higher-temperature heat storage water to be discharged from the internal space of the upper layer (114). Additionally, a temperature controller (130) is connected to the outlet (IN) side of the inlet / outlet (115) of the upper layer (114). This allows the temperature of the heat storage water to be appropriately controlled through the temperature controller (130) so that it does not become too low during the winter. The lower layer (116) is configured as a buffer layer, with the inlet (IN) of the inlet / outlet (117) connected to a water supply line to receive water supply, and heat exchanged with the upper layer (114) through a partition wall (112) to form a medium layer, thereby creating a heat storage effect. When the temperature of the lower layer (116) is above a certain level, it can be connected to be used as a medium-temperature water pipe or hot water supply through the outlet (OUT) or drain.

[0032] For example, during cooling operation, such as in the transitional season or summer, when the temperature of the buffer side reaches approximately 30 to 40°C due to cold heat storage on the heat source side, it can be discharged and used as hot water in the medium-temperature water piping. During heating operation, such as in the winter, when the temperature of the buffer side drops due to hot heat storage on the heat source side and reaches approximately 5 to 10°C, it can be discharged.

[0033] Additionally, a spiral coil (126) is installed across the upper layer (114) and lower layer (116) inside the tank (110). The spiral coil (126) is connected to the condensate insulation tank (120) through the condensate supply line (123) and the condensate recovery line (124). The condensate insulation tank (120) collects and stores the condensate that is discarded through the condensate drain line (121) of the indoor unit. The condensate is discharged to the outside through the discharge line (122). Therefore, the condensate insulation tank (120) can store the discarded condensate as waste heat and cool the heat storage water inside the simple heat storage tank (110) through the spiral coil (126) via the condensate circulation pump (125) using waste heat. For stratification of the simple heat storage tank (110), it is preferable to configure it so that it circulates from the lower layer (116) through the upper layer (114). Therefore, the simple thermal storage tank (100) can efficiently utilize not only the residual heat source but also the waste heat contained in the condensate.

[0034] The simple thermal storage tank (100) of the present invention is configured in a modular manner so that it can be easily expanded or reduced depending on the heat source conditions or heat load conditions of the environment in which the energy system is used.

[0035] FIG. 3 is a circulation diagram of a preferred embodiment of a geothermal energy system using a simple thermal storage tank according to the present invention.

[0036] Referring to FIG. 2, the geothermal energy system (200) of the present invention comprises a heat source unit (210) coupled to a first circulation unit (212) in which ground water is circulated on the primary side of a heat exchanger (220), a heat relay circulation unit (230) coupled to a second circulation unit (232) in which geothermal water is circulated on the secondary side of the heat exchanger (220), and a heat load circulation unit (not shown) each connected to the secondary side of a plurality of heat pumps (234) in which the primary side is connected in parallel to the second circulation unit (232).

[0037] The heat source unit (210) includes a geothermal source located underground that has heat of 12 to 18°C ​​regardless of the season, a geothermal circulation unit that supplies and circulates geothermal water from the geothermal source through a circulation pump and is connected to a geothermal supply pipe and a geothermal recovery pipe for heat exchange in a heat exchanger (220), and a geothermal source control unit that is provided in the geothermal supply pipe and the geothermal recovery pipe of the geothermal circulation unit to measure and control flow rate, temperature, and water level. For a detailed description, refer to Registered Patent No. 10-1993627 registered by the applicant, and a detailed description is omitted. The heat load circulation unit forms a circulation pipeline in the order of the secondary side evaporator outlet of the heat pump - compressor - condenser - expansion valve - secondary side evaporator inlet of the heat pump.

[0038] The heat transfer circulation unit (230) includes a plurality of heat pumps (234) that release heat exchanged on the indoor load side. Each heat pump (234) of the heat transfer circulation unit (230) has its primary side connected in parallel to the secondary side of the heat exchanger (210) through the second circulation unit (232). The second circulation unit (232) includes a transfer water supply pipe (232a) and a transfer water recovery pipe (232b). The transfer water supply pipe (232a) connects the secondary side outlet of the heat exchanger (220) and the primary side inlet of each heat pump (234), and the transfer water recovery pipe (232b) connects the secondary side inlet of the heat exchanger (220) and the primary side outlet of each heat pump (234). A relay circulation control unit (236) that measures and controls the flow rate, temperature, and water level is connected to the relay water supply pipe (232a) to control the circulation of the medium. The secondary side of each heat pump (234) may be a fan coil or floor heating system installed indoors.

[0039] The heat transfer circulation unit (230) is connected to the heat storage unit (240) via a bypass method through the transfer water recovery pipe (232b). Accordingly, the medium containing residual heat, which is heat-exchanged through the heat pumps (234), is recovered to the secondary side inlet of the heat exchanger (220) through the transfer water recovery pipe (232b) and is also stored in the simple heat storage tank (110) of the heat storage unit (240) connected via a bypass method. In this embodiment, the simple heat storage tank (110) is identical to the configuration described in FIG. 2 above, except that a plurality of them are connected in parallel according to the required amount of heat storage, so a detailed description is omitted.

[0040] The heat storage unit (240) is connected by bypass to the recovery pipe (232b) of the second circulation unit (232). Here, the heat pump is indirectly connected to the heat source circulation unit (210) through the heat exchanger (220), so it can be protected from contamination by groundwater.

[0041] The geothermal energy system (200) of the present invention described above obtains thermal energy through a maximum temperature difference of Δ5°C by heat exchange between the heat source circulating water of the heat source unit and the underground heat. The obtained thermal energy is supplied to a heat pump. The energy amplified through the heat pump is consumed by the heat load, and the circulating water that has generated heat, including residual heat, is stored in a simple thermal storage tank (110) connected by a bypass during the process of being recovered through a recovery pipeline. This thermal storage water serves to increase the system performance index by compensating for and controlling the heat source of the circulating water.

[0042] Therefore, in this invention, the temperature of the heat transfer medium supplied to the heat pump immediately upon initial startup can be controlled above a certain level regardless of the heat transfer delay time from the heat source during system initial startup. This allows for a reduction in the operating time of the heat pump and enables immediate heat supply without user inconvenience caused by delays in initial cooling and heating. Furthermore, when operating at partial or variable loads within the total indoor load, cooling and heating can be achieved using only the thermal storage water for a certain period. Consequently, since adaptive response to partial loads is possible, the overall power cost of the system can be reduced, thereby demonstrating energy saving effects.

[0043] The indoor load mentioned above includes all various environmental and external factors, such as the number of occupants, indoor space, and the opening and closing of doors and windows, which are used to heat and cool a building or area through the operation of a heat pump. Factors expected during the construction of a building regarding the number of occupants and a specific space are referred to as fixed loads, while factors that are difficult to predict due to frequent entry and exit of people and the frequent opening and closing of doors, such as in government offices, commercial buildings, or airports, are referred to as variable loads. Furthermore, regarding the indoor load, the above fixed load and variable load are combined to form a total load, thereby maintaining or further increasing the COP (coefficient of performance - the ratio of the refrigeration capacity in a refrigeration cycle to the work of the compressor consumed).

[0044] In the present invention, when the flow rate of the circulating medium is controlled according to the temperature difference (△T) of the geothermal water used in the heat pump, the circulating medium returned after heat exchange maintains a constant temperature, and the geothermal water exchanged with it also maintains a constant temperature upon return. Consequently, this prevents abrupt changes in the temperature of the geothermal water on the heat source side, allowing the geothermal circulation unit to operate continuously with constant efficiency without stress.

[0045] The geothermal energy system (200) configured in this way can be operated in normal mode and special mode.

[0046] During normal heating mode operation in January, the geothermal energy system (200) exchanges heat with geothermal water at 12–18°C through a heat exchanger (220) and recovers it at 7–13°C. The geothermal water from the heat exchanger (220) is introduced into the primary side of the heat pump at 10–16°C. The geothermal water, having had heat removed from the heat pump, is recovered at 5–11°C and introduced into the heat exchanger (220), while simultaneously being stored in a heat storage unit (240) connected in a bypass manner. That is, geothermal water at 10–16°C flows into each heat pump, is heat-exchanged, cooled to 7–13°C, and then discharged. In a heat pump, a circulating medium at 3–7°C, which has obtained thermal energy through a maximum temperature difference of Δ5°C, is heated to 55–60°C through a compressor, and a heating supply temperature of 45–50°C is released through floor heating coils or fan coils, and a circulating medium with a heating return temperature of 40–45°C is recovered. The recovered circulating medium is cooled to -2–2°C through an expansion valve and flows into the secondary evaporator of the heat pump.

[0047] When the geothermal source is operating normally through such heat circulation, the residual heat source of 5 to 11°C recovered from the recovery pipe of the heat relay circulation unit (230) is the ground temperature, so it can prevent a rapid drop in the ground temperature by buffering the low-temperature heat source before heat exchange with the ground. Meanwhile, when the ground heat source is insufficient during peak load, the heat storage water, whose temperature has risen by absorbing residual heat inside the recovery pipe from the heat storage tank, can be supplied to perform the role of raising the inlet temperature of the heat pump even slightly.

[0048] Special heating mode operation allows for operation using a thermal storage source instead of a geothermal source under special conditions, such as during the initial stages of system operation before the geothermal source is fully restored, during transitional seasons, or in partial load operation states where indoor heating and cooling are not operated continuously but are operated intermittently for only a short period due to severe load fluctuations.

[0049] In the special heating operation mode for January, the thermal storage unit (240) discharges thermal storage water at 28°C during heating. If the temperature of the thermal storage water inside the simple thermal storage tank (100) is lower than the temperature of the discharge condition, the thermal storage water is heated through the temperature controller (130) connected to the discharge port to control it to the target temperature. Since the temperature of the thermal storage water entering the heat pump is 28°C, the circulating medium at approximately 13-15°C becomes approximately 80-85°C after compression, and the circulating medium at 50-60°C after condensation is cooled to approximately 10-13°C after passing through the expansion valve and flows into the heat pump. Therefore, sufficient evaporation occurs without lowering the temperature of the medium below zero, so the performance index (COP) of the heat pump can be raised to 5.0 or higher. In addition, a separate defrosting operation becomes unnecessary. In conclusion, the heat storage water discharged from the primary side of the heat pump is cooled to 18°C ​​and recovered into the heat storage tank (100). The heat storage water at 18°C ​​is heated to approximately 24°C in the stratified portion within the heat storage tank (100), and at the time of discharge, it is heated to approximately 4°C by the temperature controller (130) and controlled to be discharged at approximately 28°C.

[0050] As described above, during special heating mode operation, by supplying thermal storage water at a higher temperature than ground water, it is possible to supply heating and cooling rapidly during the initial stages of system operation until the ground heat source stabilizes, and it enables continuous heating and cooling without interruption during transitional seasons or sudden load fluctuations. In addition, when it is impossible to supply heat using only the heat source from the simple thermal storage tank, the stored heat source is prioritized for supplying to the heat pump, and the ground heat source is pumped and supplemented only as much as necessary, thereby enabling heat supply with minimal power and increasing the system's COP.

[0051] Figure 4 is a table showing data measured for 10 hours in January using the energy system of Figure 3.

[0052] Referring to FIG. 4, it can be seen that in the special heating mode for January, the upper layer (114) of the simple thermal storage tank (110) has an average inlet temperature of 18.3°C and an average outlet temperature of 28.4°C. In the lower layer (116), it can be seen that tap water with an average temperature of 12.6°C is inlet and water with an average temperature of 7.4°C is outlet. By using thermal storage water with a higher temperature than the underground heat source water of 15°C, the power consumption of the heat pump can be reduced, and it can be seen that the performance index (COP) relative to power consumption increases to about 5.0 compared to the existing 4.0. It can be seen that the temperature of the condensate entering and exiting the condensate insulation tank in January is 7.55°C.

[0053] The following describes the cooling mode of the present invention.

[0054] In the normal cooling mode of August, the geothermal energy system (200) absorbs heat from groundwater at 15–25°C through a heat exchanger (220) and recovers it at 25–32°C. The groundwater from which heat has been removed in the heat exchanger (220) is introduced into the primary side of the heat pump at 20–28°C. The groundwater that has absorbed heat from the heat pump is recovered at 25–35°C and introduced into the heat exchanger (220), and at the same time is stored in the heat storage unit (240) connected in a bypass manner. That is, groundwater at 20–28°C flows into the primary side of each heat pump, undergoes heat exchange, absorbs heat at 25–35°C, and is discharged.

[0055] On the secondary side of the heat pump, a circulating medium with a cooling supply temperature of 7 to 10°C is supplied to the indoor unit and absorbs heat from the room, entering the secondary side at approximately 12 to 15°C.

[0056] Inside the heat pump, low-temperature gas of 5 to 10°C that has passed through the evaporator is compressed by a compressor to discharge high-temperature, high-pressure heated steam of 70 to 90°C. High-temperature liquid of 35 to 45°C that has passed through the condenser passes through an expansion valve, where it is converted into low-temperature, low-pressure gas of about 3 to 5°C and supplied to the evaporator.

[0057] Therefore, the heat pump extracts heat from the water circulated indoors at 12–15°C and sends it into the ground, and finally, water at 25–32°C enters the ground and is cooled by the ground temperature of 15–20°C.

[0058] As such, in normal cooling mode, the thermal storage unit stores heat as the stored water converges to approximately 30°C. Therefore, although the temperature is too low for high-temperature hot water supply, it can be used for hot water preheating to raise the constant temperature from 15°C to 35°C. Additionally, since some heat is absorbed in the thermal storage tank before reaching the underground heat exchanger, it prevents the underground temperature from rising excessively, which helps maintain cooling performance.

[0059] When operating in the special cooling mode in August, the heat stored in the heat storage tank of the heat storage unit is used as a heat source and supplied to the primary side of the heat pump. Although the temperature of the return water entering the heat storage tank is about 33°C, the temperature of the heat stored in the heat storage tank is cooled down to about 17°C using the discarded condensate at about 13°C, and when the water is discharged from the heat storage tank, it is further lowered to about 13°C by the temperature controller (130) and supplied as a heat source water to the primary side of the heat pump. Therefore, since the heat pump uses 13°C, which is much lower than the ground water of 15~20°C during normal operation, as a heat source, the refrigerant can be easily liquefied, thereby maximizing condensation efficiency. In addition, as the condensation pressure is lowered, the load on the compressor is reduced, so the power consumption of the compressor can be significantly reduced.

[0060] Inside the heat pump, low-temperature gas of 5 to 10°C that has passed through the evaporator is compressed by a compressor to discharge high-temperature, high-pressure heated steam of 65 to 80°C. High-temperature liquid of 20 to 25°C that has passed through the condenser passes through an expansion valve, where it is converted into low-temperature, low-pressure gas of about 3 to 5°C and supplied to the evaporator.

[0061] Therefore, since the heat source temperature is very low at 13℃, the discharge temperature is lower than during normal cooling, resulting in significantly improved compressor efficiency. Additionally, because the refrigerant can be cooled rapidly, the condensation temperature is formed at a considerably low level, acting as a decisive factor in increasing system efficiency. In other words, since the heat source temperature in the special cooling mode is lower than in the normal cooling mode, resulting in lower condensation pressure, power consumption can be reduced by approximately 15–20% or more.

[0062] In this embodiment, the condensate is collected in an insulated tank and, if necessary, supplied to a simple thermal storage tank to lower the temperature of the stored water. This waste cold energy recovery method can further increase condensation efficiency, and since the cold condensate offsets a portion of the heat that would otherwise be wasted into the ground in normal mode, it is possible to reduce the size of the ground heat exchanger or suppress the rise in ground temperature. Furthermore, it is environmentally friendly because the condensate, which would otherwise be simply discarded through a drain, is recycled as a heat medium.

[0063] Figure 5 is a table showing data measured for 10 hours in August using the energy system of Figure 3.

[0064] Referring to FIG. 5, it can be seen that in the August cooling mode, the inlet temperature of the upper layer (114) of the simple thermal storage tank (110) is 33.1°C and the outlet temperature is 13.1°C. It can be seen that the lower layer (116) receives an average of 19.1°C of water and discharges an average of 29.9°C. It can be seen that the discharge water from the upper layer is cooled by 13.1°C due to the waste heat of the condensate and the water from the lower layer. It can be seen that the inlet temperature of the condensate entering the August condensate insulation tank is 12.67°C and the outlet temperature is 25.77°C. The flow rate is about 230 lpm higher than the flow rate of the upper layer of the thermal storage tank. That is, it can be seen that in the August cooling mode, the condensate is used to cool the thermal storage water of the thermal storage tank.

[0065] Therefore, by using the cold water from the thermal storage tank, the power consumption of the heat pump can be reduced, and it can be seen that the performance index (COP) relative to power consumption is increased to about 5.3 compared to the existing 4.1.

[0066] FIG. 6 shows a circulation diagram of a preferred embodiment of an air heat energy system using a simple thermal storage tank according to the present invention.

[0067] The air source energy system (300) of the present invention comprises an outdoor unit (310) (heat source circulation unit) coupled to a first circulation unit in which a first heat transfer medium circulates on the primary side of a heat exchanger (320), and a heat relay circulation unit (330) coupled to a second circulation unit in which a second heat transfer medium circulates on the secondary side of the heat exchanger (320). The heat relay circulation unit (330) comprises a plurality of heat pumps (334) in which the primary side is each coupled to the secondary side of the heat exchanger (320) to allow heat circulation and each heat load is each coupled to the secondary side, a medium control unit that controls the circulation of the second heat transfer medium flowing through the second circulation unit, and a heat storage unit (240).

[0068] The air source energy system (300) of the present invention differs from the geothermal energy system (200) described above in that the configuration of the heat source part is different, while the remaining configuration is the same, so a detailed description is omitted. Likewise, the air source energy system (300) also enables heating and cooling control with a high coefficient of performance using the heat stored in the heat storage tank, regardless of the air source, by storing or cooling residual heat or waste heat in the simple heat storage tank (110).

[0069] The terms and words used in the specification and claims described above should not be interpreted as being limited to their ordinary or dictionary meanings, and should be interpreted in a meaning and concept consistent with the technical spirit of the invention, based on the principle that the inventor can appropriately define the concept of the terms to best describe his invention.

[0070] Therefore, it should be understood that the configurations illustrated in the drawings and embodiments described in this specification are merely one of the most preferred embodiments of the present invention and do not represent all of the technical ideas of the present invention, and that various equivalents and modifications capable of replacing them may exist at the time of filing this application. Explanation of the symbols

[0071] 10, 210, 310: Heat source circulation section 20, 230, 330: Heat relay circulation section 30: Heat load circulation section 40, 240, 340: Heat storage section 50 : Control unit 110 : Simple heat storage tank 120 : Condensate insulation tank 130 : Temperature controller 200: Geothermal Energy Systems 300 : Air source energy system

Claims

Claim 1 A heat source circulation unit (10); a plurality of heat load circulation units (30, 32, 34, 36) in which each heat load independently forms a circulation system and can be selectively operated; a heat relay circulation unit (20) that heat-couples the plurality of heat load circulation units (30) in parallel to exchange the heat energy of the heat source circulation unit (10) with the plurality of heat load circulation units (30) in common, and the heat relay circulation unit (20) is provided with a heat storage unit (40) for storing at least one of the residual heat source and waste heat recovered from the plurality of heat load circulation units (30), and in a normal operation mode, at least one of the recovered residual heat source and waste heat is stored in the heat storage unit (40), and in a special operation mode, the heat energy stored in the heat storage unit (40) is used to control the plurality of heat load circulation units (30) to exchange heat in common, and the control unit (50) is provided. The heat storage unit (40) is composed of at least one vertically elongated simple heat storage tank (110), and each simple heat storage tank (110) is divided into an upper layer and a lower layer by a partition wall, and the lower layer is used as a buffer layer, and the mature heat storage water of the upper layer is connected by a bypass to the heat relay circulation unit (20), and the simple heat storage tank (110) is provided with condensate through a coil pipe (126) that extends spirally from the lower layer to the upper layer, and the condensate is provided from a condensate insulation tank (120). The condensate that is discarded through the condensate drain line (121) from each of the indoor units of the plurality of heat load circulation units (30, 32, 34, 36) above. Energy system characterized by Claim 2 delete Claim 3 delete Claim 4 An energy system according to claim 1, wherein the above-mentioned simple thermal storage tank is combined with a temperature controller capable of controlling the temperature of the thermal storage water discharged at the outlet side of the upper layer. Claim 5 An energy system according to claim 1, wherein the heat source is either geothermal heat or air heat.

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