The present invention relates to a heat exchange system and a heat load control system.
LNG (Liquefied Natural Gas) is obtained by removing nitrogen, carbon dioxide, and impurities from natural gas, which is a gas, for the sake of convenient transportation in overseas gas fields and then liquefying the natural gas at a low temperature and a high pressure, and is composed of methane, propane, butane, and so on. A storage density of LNG is about 430 kg/m3 to about 470 kg/m3, which is 625 times higher than a storage density of a gas in a standard state, and is in a cryogenic liquid state with a temperature of −162° C. LNG is imported from an overseas gas field through an LNG vessel and then unloaded and stored in an LNG storage tank of an LNG terminal. Thereafter, the LNG is vaporized to be transported to a house, but there is a problem in that cold-heat generated during vaporization of LNG may not be used properly.
Meanwhile, a data center refers to a facility that collects equipment required to provide IT services, such as servers, networks, and storage, in one building, operates 24 hours a day and 365 days a year, and manages the equipment in an integrated manner. The servers, networks, and storage devices placed in the data center generate much heat, and since the devices have to maintain an appropriate temperature for normal operation, a device for regulating a temperature of the data center is required. However, the related art only uses a separate energy to control the temperature of the data center, and there is no attempt to use cold-heat generated during the process of vaporization of LNG.
NG (Natural Gas) is vaporized to be transported to homes, and cold-heat generated during vaporization of LNG may be exchanged with waste heat of a factory or a data center.
However, there is a problem in that the amount of cold-heat generated during a vaporization process of LNG is different from the amount of waste heat of a factory, a data center, or so on, and thereby, loads of a heat exchange system are mismatched. The system according to the related art has no technology capable of preventing the mismatch of loads due to a difference in calorific value between two heat sources.
In addition, the related art has no means for supplying or absorbing heat when a system stops in an emergency such as power interruption, and thus, there is a problem in that heat exchange is stopped in an emergency.
The present invention is to solve the problem of the related art described above, and an aspect of the present invention relates to a heat exchange system capable of effectively controlling a heat exchange between a first medium and a second medium by including first and second adjustment means and heat absorption means to adjust a temperature and a pressure of a working fluid.
The present invention is to solve the problem of the related art described above, and one aspect of the present invention relates to a heat load control system capable of absorbing a difference in the amount of heat between cold-heat supplied to a working fluid from a first heat exchanger and heat supplied to the working fluid from a second heat exchanger by using heat dissipation means, heat supply means, adjustment means, an ice thermal storage system, and a heater.
A heat exchange system according to the present invention includes a pump or a compressor that pressurizes a working fluid, a first heat exchanger that receives the working fluid from the pump or the compressor causes the working fluid to exchange heat with a first medium to decrease a temperature of the working fluid, first adjustment means for receiving the working fluid from the first heat exchanger and decreasing a temperature and a pressure of the working fluid, heat absorption means for receiving the working fluid from the first adjustment means and absorbing heat to supply the heat to the working fluid, second adjustment means for receiving the working fluid from the heat absorption means and decreasing the temperature and the pressure of the working fluid, and a second heat exchanger that receives the working fluid from the second adjustment means and causes the working fluid to exchange heat with a second medium to increase the temperature of the working fluid and transfers the working fluid to the pump or compressor.
In addition, in the heat exchange system according to the present invention, the first adjustment means includes a first expansion valve that receives the working fluid from the first heat exchanger and decreases the pressure of the working fluid, and a first capillary tube that receives the working fluid from the first expansion valve and decreases a temperature and a pressure of the working fluid.
In addition, in the heat exchange system according to the present invention, the second adjustment means includes a second capillary tube that receives the working fluid from the heat absorption means and decreases a temperature and a pressure of the working fluid, and a second expansion valve that receives the working fluid from the second capillary tube and decreases the pressure of the working fluid.
In addition, the heat exchange system according to the present invention further incudes a first bypass line for transferring the working fluid from the first heat exchanger to the heat absorption means so as to avoid the first adjustment means.
In addition, the heat exchange system according to the present invention further includes a second bypass line for transferring the working fluid from the heat absorption means to the second heat exchanger so as to avoid the second adjustment means.
In addition, in the heat exchange system according to the present invention, the heat absorption means has a fin-pipe structure.
In addition, in the heat exchange system according to the present invention, the heat absorption means includes a plurality of plate portions arranged side by side, each being formed in a flat plate shape, and a tube portion which extends in one direction to penetrate the plurality of plate portions and then is bent and then extends in the other direction to penetrate the plurality of plate portions, and through which the working fluid passes.
In addition, in the heat exchange system according to the present invention, the first medium is liquefied natural gas (LNG), and the first medium absorbs heat while exchanging heat with the working fluid in the first heat exchanger.
In addition, in the heat exchange system according to the present invention, the second medium is internal air of a data center, a large shopping mall, or a refrigeration warehouse, and the second medium dissipates heat while exchanging heat with the working fluid in the second heat exchanger.
In addition, in the heat exchange system according to the present invention, the heat absorption means absorbs heat from the internal air of the data center, the large shopping mall, or the refrigeration warehouse.
In addition, in the heat exchange system according to the present invention, when the internal air of the data center, the large shopping mall, or the refrigeration warehouse includes first internal air at a temperature higher than or equal to the predetermined temperature and the second internal air at a temperature lower than the predetermined temperature, the first internal air exchanges heat with the working fluid in the second heat exchanger, and the second internal air supply heat to the working fluid in the heat absorption means.
A heat load control system according to the present invention includes pressurized means for pressurized a working fluid, a first heat exchanger that causes the working fluid to exchange heat with the first medium and transfers cold-heat of the first medium to the working fluid, the second heat exchanger that causes the working fluid to exchange heat with the second medium and transfers heat of the second medium to the working fluid, heat dissipation means provided between the first heat exchanger and the second heat exchanger to dissipate heat from the working fluid, heat supply means provided between the first heat exchanger and the second heat exchanger to supply heat to the working fluid, adjustment means provided between the first heat exchanger and the second heat exchanger to decrease a temperature and a pressure of the working fluid, an ice thermal storage system provided between the first heat exchanger and the second heat exchanger to supply cold-heat to the working fluid or to absorb the cold-heat from the working fluid, and a heater connected to the first heat exchanger to supply heat to the working fluid.
In addition, in the heat load control system according to the present invention, the adjustment means includes an expansion valve for decreasing the pressure of the working fluid, and a capillary tube for decreasing the temperature and the pressure of the working fluid.
In addition, in the heat load control system according to the present invention, the heat dissipation means or the heat supply means has a fin-pipe structure.
In addition, in the heat load control system according to the present invention, the heat dissipation means or the heat supply means includes a plurality of plate portions arranged side by side, each being formed in a flat plate shape, and a tube which extends in one direction to penetrate the plurality of plate portions and then is bent and then extends in the other direction to penetrate the plurality of plate portions, and through which the working fluid passes.
In addition, in the heat load control system according to the present invention, the heat dissipation means or the heat supply means includes a fan for inducing a forced convection.
In addition, in the heat load control system according to the present invention, the working fluid selectively passes through at least one of the heat dissipation means, the heat supply means, the adjustment means, and the ice thermal storage system.
In addition, in the heat load control system according to the present invention, the first medium is liquefied natural gas (LNG), and the first medium supplies cold-heat to the working fluid in the first heat exchanger.
In addition, in the heat load control system according to the present invention, the second medium is a fluid or seawater that receives heat from waste heat of a factory, waste heat of a garbage disposal site, waste heat of a data center, or waste heat of a shopping mall, and the second medium supplies heat to the working fluid in the second heat exchanger.
In addition, in the heat load control system according to the present invention, the heat dissipation means dissipates heat from the working fluid to atmosphere.
In addition, in the heat load control system according to the present invention, the heat supply means supplies heat from internal heat of a building to the working fluid.
In addition, in the heat load control system according to the present invention, the heater is an electric heater, a gas boiler using BOG (Boil Off Gas), or a heater using waste heat of a data center.
In addition, in the heat load control system according to the present invention, when the amount of cold-heat of the first medium is greater than the amount of heat of the second medium by a first predetermined value, the ice thermal storage system absorbs cold-heat from the working fluid, or the heat supply means supplies heat to the working fluid, and when the second predetermined value is greater than the first predetermined value, in a case where the cold-heat of the first medium is greater than the heat of the second medium by the second predetermined value, the heater supplies heat to the working fluid, and when a third predetermined value is greater than the second predetermined value, in a case where the amount of cold-heat of the first medium is greater than the amount of heat of the second medium by the third predetermined value, the heat supply means supplies heat to the working fluid, and the heater supplies heat to the working fluid, and when a the fourth predetermined value is greater than the third predetermined value, in a case where the amount of cold-heat of the first medium is greater than the amount of heat of the second medium by the fourth predetermined value, the ice thermal storage system absorbs cold-heat from the working fluid, the heat supply means supplies heat to the working fluid, and the heater supplies heat to the working fluid.
In addition, in the heat load control system according to the present invention, when the amount of heat of the second medium is greater than the amount of cold-heat of the first medium by a the fifth predetermined value, the ice thermal storage system supplies cold-heat to the working fluid, or the heat dissipation means dissipates heat from the working fluid, and when the sixth predetermined value is greater than the fifth predetermined value, in a case where the amount of heat of the second medium is greater than the amount of cold-heat of the first medium by the sixth predetermined value, the ice thermal storage system supplies cold-heat to the working fluid, and the heat dissipation means dissipates heat from the working fluid.
In addition, in the heat load control system according to the present invention, a diameter of a tube of the heat supply means through which the working fluid passes is larger than a diameter of a tube of the heat dissipation means through which the working fluid passes.
Features and advantages of the present invention will become more apparent from the following detailed description taken in conjunction with the accompanying drawings.
Prior to this, terms or words used in the present specification and claims should not be construed as usual and dictionary meanings and should be construed as meaning and concept consistent with the technical idea of the present invention, based on a principle that the inventor may adequately define the concept of the terms in order to best describe his/her invention.
According to the present invention, there is an advantage in that process of heat exchange between the first medium and a second medium may be effectively controlled by adjusting a temperature and a pressure of a working fluid by including the first and the second adjustment means and heat absorption means.
According to the present invention, there is an advantage in that a load of a heat exchange system may be prevent from mismatching due to a difference in the amount of heat by absorbing a difference in the amount of heat between cold-heat of a first medium supplied to a working fluid in the first heat exchanger and heat of the second medium supplied to the working fluid in a second heat exchanger by using heat dissipation means, heat supply means, adjustment means, an ice thermal storage system, a heater, and so on.
In addition, according to the present invention, there is an effect that heat exchange between a working fluid and first and second media may be made in first and second heat exchangers even in an emergency by supplying cold-heat to the working fluid by using an ice thermal storage system in an emergency such as power interruption.
Objects, specific advantages, and novel features of the present invention will become more apparent from the following detailed description and preferred embodiments taken in conjunction with the accompanying drawings. In the present specification, it should be noted that, in attaching reference numbers to components of each drawing, only the same components are given the same number as possible even though the components are illustrated in different drawings. In addition, terms such as “first” and “second” are used to distinguish one component from another component, and the components are not limited by the terms. Hereinafter, in describing the present invention, detailed descriptions of related known technologies that may unnecessarily obscure the subject matter of the present invention will be omitted.
Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.
As illustrated in
The pump or the compressor 100 serves to increase a pressure by pressurized a working fluid. The pump or the compressor 100 may pressurize the working fluid and transfer the working fluid to the first heat exchanger 200. Accordingly, the working fluid decreases in pressure while passing through the pump or compressor 100. At this time, the working fluid may be in a gaseous state. Meanwhile, the working fluid is not limited in particular, but may be, for example, glycol, propane, ammonia, or so on.
The first heat exchanger 200 serves to exchange heat between the working fluid and a first medium. Specifically, the working fluid is transferred from the pump or the compressor 100 to the first heat exchanger 200, and the first medium is transferred thereto, and the working fluid and the first medium exchange heat with each other. At this time, since a temperature of the first medium is lower than a temperature of the working fluid, the temperature of the working fluid is decreased through the heat exchange. That is, the working fluid emits heat while exchanging heat with the first medium in the first heat exchanger 200. In contrast to this, since the temperature of the working fluid is higher than the temperature of the first medium, the temperature of the first medium is increased through the heat exchange. That is, the first medium absorbs heat while exchanging heat with the working fluid in the first heat exchanger 200. Meanwhile, when the temperature of the first medium increases in the first heat exchanger 200, the first medium may phase-change from a liquid to a gas. For example, the first medium may be liquefied natural gas (LNG) that maintains a pressure of about 70 bar and a temperature of about −163° C. and may phase-change to compressed natural gas (CNG) while increasing in temperature in the first heat exchanger 200.
The first adjustment means 300 receives a working fluid from the first heat exchanger 200 and serves to decrease a temperature and a pressure of the working fluid. Here, the first adjustment means 300 may include the first expansion valve 310 and the first capillary tube 320. Specifically, the first expansion valve 310 receives the working fluid from the first heat exchanger 200 and decreases a pressure of the working fluid. In addition, the first capillary tube 320 receives the working fluid from the first expansion valve 310 and decreases a temperature and a pressure of the working fluid. As a result, the working fluid may be decreased in pressure while passing through the first expansion valve 310 and decreases in temperature and pressure while passing through the first capillary tube 320.
The heat absorption means 400 receives a working fluid from the first adjustment means 300 and serves to supply heat to the working fluid. Here, the heat absorption means 400 absorbs heat from the outside and supplies the heat to the working fluid and may be, for example, a fin-pipe structure. As illustrated in
The second adjustment means 500 (refer to
The second heat exchanger 600 serves to exchange heat between the working fluid and the second medium. Specifically, the second heat exchanger 600 receives the working fluid from the second adjustment means 500 and receives the second medium, and the working fluid and the second medium exchange heat with each other. At this time, since a temperature of the second medium is higher than a temperature of the working fluid, the temperature of the working fluid is increased through heat exchange. That is, the working fluid absorbs heat while exchanging heat with the second medium in the second heat exchanger 600. In contrast to this, since the temperature of the working fluid is lower than the temperature of the second medium, the temperature of the second medium is decreased through the heat exchange. That is, the second medium emits heat while exchanging heat with the working fluid in the second heat exchanger 600. For example, the second medium may be the internal air of a data center. Since a large amount of heat is generated from a server, a network, and a storage in the data center, a temperature of the internal air is relatively high. Accordingly, the internal air (second medium) of the data center may emit heat while exchanging heat with the working fluid in the second heat exchanger 600. As a result, the temperature of the internal air of the data center may be maintained at an appropriate temperature through the process of heat-exchange with the working fluid.
More specifically, in the data center, temperatures of the internal air in each zone may be different from each other. Accordingly, the internal air of the data center may include the first internal air having a temperature equal to or higher than the predetermined temperature and the second internal air having a temperature lower than the predetermined temperature. At this time, the first internal air having a relatively high temperature may exchange heat with the working fluid in the second heat exchanger 600, and the second internal air having a relatively low temperature may supply heat to the working fluid from the heat absorption means 400. Accordingly, the working fluid increases in temperature to a predetermined value by receiving heat from the second internal air having a relatively low temperature in the heat absorption means 400, and then may increase in temperature above a predetermined value by receiving heat from the first internal air having a relatively high temperature in the second heat exchanger 600.
However, the second medium is not limited to the internal air of the data center and may also be the internal air of a large shopping mall, the internal air of a refrigeration warehouse, and so on, which has a large cooling demand.
Overall, the heat exchange system according to the present embodiment may decrease in temperature because the working fluid exchanges heat with a first medium (liquefied natural gas) having a relatively low temperature in the first heat exchanger 200 and may decrease a temperature of a second medium (for example, internal air or so on of a data center) because the working fluid having the decreased temperature exchanges heat with the second medium (for example, internal air or so on of the data center) having a relatively high temperature in the heat exchanger 600. In summary, the second medium (internal air or so on of the data center) by using cold-heat of the first medium (liquefied natural gas).
Additionally, the heat exchange system according to the present embodiment may further include a first bypass line 700 and a second bypass line 800. Here, the first bypass line 700 transfers a working fluid from the first heat exchanger 200 to the heat absorption means 400 so as to avoid the first adjustment means 300. That is, the first bypass line 700 connects between the first heat exchanger 200 and the first adjustment means 300 and between the first adjustment means 300 and the heat absorption means 400, and thereby, the working fluid is transferred from the first heat exchanger 200 to the heat absorption means 400 without passing through the first adjustment means 300. In addition, the second bypass line 800 transfers the working fluid from the heat absorption means 400 to the second heat exchanger 600 so as to avoid the second adjustment means 500. That is, the second bypass line 800 connects between the heat absorption means 400 and the second adjustment means 500 and between the second adjustment means 500 and the second heat exchanger 600, and thereby, the working fluid is transferred from the heat absorption means 400 to the second heat exchanger 600 without passing through the second adjustment means 500. Due to the first bypass line 700 and the second bypass line 800, the working fluid may not selectively pass through the first adjustment means 300 and the second adjustment means 500. For example, when the first bypass line 700 operates, the working fluid may be transferred in the order of the pump or the compressor 100→the first heat exchanger 200→the first bypass line 700→the heat absorption means 400→the second adjustment means 500→the second heat exchanger 600. In addition, when the second bypass line 800 operates, the working fluid may be transferred in the order of the pump or the compressor 100→the first heat exchanger 200→the first adjustment means 300→the heat absorption means 400→the second bypass line 800→the second heat exchanger 600.
A working fluid in a gaseous state increases in pressure while passing through the pump or the compressor 100. At this time, a pressure increases in a P-h line diagram ({circle around (1)} in
In the heat exchange system according to the present embodiment, the working fluid decreases in temperature and pressure while passing through the first and second capillary tubes 320 and 520, thereby decreasing enthalpy as much as possible before the working fluid passes through the second heat exchanger 600. Accordingly, the working fluid may have a greater amount of heat absorbed by the second heat exchanger 600 compared to the amount of heat emitted from the first heat exchanger 200 (although the working fluid absorbs heat from the heat absorption means 400, the amount of heat absorbed by the second heat exchanger 600 may be greater than the amount of heat emitted from the first heat exchanger 200). It can be confirmed that a difference in enthalpy (Δh2 in
In addition, the heat exchange system according to the present embodiment includes the first and second expansion valves 310 and 510 and the first and second capillary tubes 320 and 520, thereby decreasing a pressure of the working fluid as much as possible before the working fluid passes through the second heat exchanger 600. As described above, the second heat exchanger 600 absorbs heat of a second medium in a state where a pressure of the working fluid is as low as possible, and thus, the efficiency of heat absorption may be increased (because the lower the pressure, the higher the amount of heat absorption per hour).
In addition, the heat exchange system according to the present embodiment includes the first and second adjustment means 300 and 500 and the heat absorption means 400, and thus, an operation region of a working fluid may be selected. For example, as illustrated in
As a result, depending on the degree of decrease in pressure of the working fluid generated while passing through the first expansion valve 310, the working fluid may operate in a liquid state (a pressure is decreased to a predetermined value, {circle around (3)} in
In detail, according to the amount of heat of a working fluid emitted from the first heat exchanger 200, the working fluid may be in a liquid state or wet steam (liquid+gas) state, and by adjusting a decrease in pressure generated by the first and second expansion valves 310 and 510, or by adjusting lengths or diameters of the first and second capillary tubes 320 and 520, an operation region or the type of the working fluid to be used may be selected.
A working fluid in a gaseous state increases in pressure while passing through the pump or the compressor 100. At this time, the pressure increases in the P-h line diagram ({circle around (1)} in
In addition, as illustrated in
In this case, since the area in which the working fluid operates in the liquid state is increased, the overall heat exchange system may be adjusted or the working fluid may be selected to correspond thereto. For example, propane capable of operating in the supercooling region may be used as the working fluid.
A working fluid in a gaseous state increases in pressure while passing through the pump or the compressor 100. At this time, the pressure increases in the P-h line diagram ({circle around (1)} in
In this case, a region in which the working fluid operates in a liquid state may be minimized, and a region in which the working fluid operates in a wet steam (liquid+gas) state may be increased because the size of the P-h diagram below is wider.
In addition, as illustrated in
In this case, a region in which the working fluid operates in a liquid state may be maximized, and a region in which the working fluid operates in a wet steam (liquid+gas) state may be reduced.
As a result, according to the amount of heat absorbed by the working fluid in the first heat exchanger 200, the working fluid may be selectively operated in either a wet steam (liquid+gas) state or a liquid state.
As illustrated in
The pressurized means 100 serves to increase a pressure by pressurized a working fluid. That is, the working fluid increases in pressure while passing through the pressurized means 100. In this case, the working fluid may be in a gaseous state or a liquid state, and the type of the working fluid is not limited in particular, but the working fluid may be, for example, propane, glycol, ammonia, or so on. Meanwhile, the pressurized means 100 is not limited in particular, but may include a pump 110 and a compressor 120. For example, when the working fluid is in a liquid state, the working fluid may be increased in pressure by being pressurized by the pump 110, and when the working fluid is in a gaseous state, the working fluid may be increased in pressure by being pressurized by the compressor 120.
The first heat exchanger 200 serves to exchange heat between a working fluid and a first medium. Specifically, the working fluid and the first medium are transferred to the first heat exchanger 200, and cold-heat of the first medium is transferred to the working fluid. At this time, since a temperature of the first medium is lower than a temperature of the working fluid, the temperature of the working fluid is decreased through heat exchange. In contrast to this, since the temperature of the working fluid is higher than the temperature of the first medium, the temperature of the first medium is increased through the process of heat exchange. For example, the first medium may be liquefied natural gas (LNG) that maintains a pressure of about 70 bar to about 250 bar and a temperature of about −163° C., and increases in temperature in the first heat exchanger 200 to be phase-changed (evaporated) to compressed natural gas (CNG). As a result, the liquefied natural gas which is the first medium is vaporized in the first heat exchanger 200 and may supply cold-heat to the working fluid.
The second heat exchanger 300 serves to exchange heat between a working fluid and a second medium. Specifically, the working fluid and the second medium are transferred to the second heat exchanger 300, and heat of the second medium is transferred to the working fluid. At this time, since a temperature of the second medium is higher than a temperature of the working fluid, the temperature of the working fluid is increased through heat exchange. In contrast to this, since the temperature of the working fluid is lower than the temperature of the second medium, the temperature of the second medium is decreased through the process of heat-exchange. For example, the second medium may be a fluid that receives heat from waste heat of a factory, waste heat of a garbage disposal site, waste heat of a data center, or waste heat of a shopping mall. In addition, the second medium may be seawater. The waste heat of the factory, the waste heat of the garbage disposal site, the waste heat of the data center, the waste heat of the shopping mall, the seawater, or so on are relatively hot. As a result, the waste heat of the factory, the waste heat of the waste garbage disposal site, the waste heat of the data center, the waste heat of the shopping mall, the seawater, or so on (the second medium), which have a relatively high temperature, may be decreased in temperature to supply heat to the working fluid.
As a result, in the heat load control system according to the present embodiment, as the cold-heat of the first medium is exchanged with the heat of the second medium through the working fluid, the first medium (liquefied natural gas) increases in temperature to be vaporized, and at the same time, the second medium (a fluid or seawater that receives heat from the waste heat of the factory, the waste heat of the garbage disposal site, the waste heat of the data center, or the waste heat of the shopping mall, etc.). That is, a factory, a garbage disposal site, a data centers, a shopping mall, or seawater related to the second medium may be cooled by using the cold-heat of the first medium (liquefied natural gas), and the first medium (liquefied natural gas) may be vaporized by using the heat of the second medium.
The heat dissipation means 400 serves to dissipate heat from the working fluid. Here, the heat dissipation means 400 absorbs heat from the working fluid and discharges the heat to the outside, and for example, the heat dissipation means 400 may dissipate heat from the working fluid to ambient air. Meanwhile, the heat dissipation means 400 may have a fin-pipe structure. As illustrated in
The heat supply means 500 serves to supply heat to the working fluid. Here, the heat supply means 500 absorbs heat from the outside and supplies the heat to the working fluid, and for example, the heat supply means 500 may supply heat from internal heat of the building to the working fluid. Meanwhile, the heat supply means 500 may have a fin-pipe structure, like the heat dissipation means 400. As illustrated in
The adjustment means 600 serves to decrease temperature and pressure of the working fluid. Here, the adjustment means 600 may include expansion valves 610a to 610d and capillary tubes 620a to 620d. At this time, the expansion valves 610a to 610d decrease a pressure of the working fluid, and the capillary tubes 620a to 620d decrease temperature and pressure of the working fluid. Accordingly, the working fluid may decrease in pressure while passing through the expansion valves 610a to 610d and may decrease in temperature and pressure while passing through the capillary tubes 620a to 620d.
More specifically, the adjustment means 600 may include first to the fourth adjustment means 600a to 600d. Here, the first adjustment means 600a may include a the first expansion valve 610a and the first capillary tube 620a provided in a first auxiliary line 10a (for example, an inlet side) of the heat dissipation means 400, and the second adjustment means 600b may include the second expansion valve 610b and the second capillary tube 620b provided in the second auxiliary line 10b (for example, an outlet side) of the heat dissipation means 400. In addition, the third adjustment means 600c may include the third expansion valve 610c and the third capillary tube 620c provided in a third auxiliary line 10c (for example, an inlet side) of the heat supply means 500, and the fourth adjustment means 600d may include the fourth expansion valve 610d and the fourth capillary tube 620d provided in the fourth auxiliary line 10d (for example, an outlet side) of the heat supply means 500. That is, the adjustment means 600 may be provided on the inlet side and the outlet side of the heat dissipation means 400 and on the inlet side and the outlet side of the heat supply means 500, respectively.
The ice thermal storage system 700 serves to absorb cold-heat from a working fluid or supply the cold-heat to the working fluid.
Here, the ice thermal storage system 700 absorbs cold-heat while changing a liquid phase to a solid phase or supplies cold-heat while changing the solid phase to the liquid phase. That is, the ice thermal storage system 700 may absorb cold-heat from a working fluid while changing the liquid phase to the solid phase and may supply the cold-heat to the working fluid while changing the solid phase to the liquid phase. In contrast to this, the working fluid may decrease in temperature by absorbing cold-heat while passing through the ice thermal storage system 700 or may increase in temperature by supplying cold-heat. Here, the ice thermal storage system 700 may be used to absorb cold-heat from a working fluid when the amount of cold-heat of a first medium is greater than the amount of heat of a second medium or may be used to supply cold-heat to a working fluid when the amount of heat of the second medium is greater than the amount of cold-heat of the second medium, and details thereof will be described below.
The heater 800 serves to supply heat to a working fluid. Here, the heater 800 is connected to the first heat exchanger 200 to supply heat to the working fluid when the working fluid exchanges heat with the first medium while passing through the first heat exchanger 200. At this time, the working fluid receives heat by the heater 800, thereby increasing in temperature. Here, the heater 800 is not limited in particular but may be, for example, an electric heater, a gas boiler, or a heater using waste heat of a data center. At this time, the gas boiler may use BOG (Boil Off Gas) of liquefied natural gas (first medium). Here, the heater 800 may be used to supply heat to the working fluid when the amount of cold-heat of the first medium is greater than the amount of heat of the second medium, and details thereof will be described below.
Overall, in the heat load control system according to the present embodiment, when there is a difference in the amount of heat between the cold-heat of the first medium supplied to the working fluid from the first heat exchanger 200 and the heat of the second medium supplied to the working fluid from the second heat exchanger 300, the difference in the amount of heat is absorbed by using the heat dissipation means 400, the heat supply means 500, the adjustment means 600, the ice thermal storage system 700, and the heater 800, and thus, mismatch of a load of the heat exchange system may be prevented from occurring due to the difference in the amount of heat.
Meanwhile, in the heat load control system according to the present embodiment, the working fluid may be transferred through a main line 10 connecting the first heat exchanger 200 to the second heat exchanger 300 and may be transferred to the pressurized means 100, the heat dissipation means 400, the heat supply means 500, the adjustment means 600, the ice thermal storage system 700, and so on through the auxiliary lines branched from the main line 10. Here, the auxiliary lines may include first to tenth auxiliary lines 10a to 10j branched from the main line 10. Specifically, the first and second auxiliary lines 10a and 10b connect an inlet side and an outlet side of the heat dissipation means 400 to the main line 10, and the third and fourth auxiliary lines 10c and 10d connect an inlet side and an outlet side of the heat supply means 500 to the main line 10. In addition, the fifth and sixth auxiliary lines 10e and 10f connect an inlet side and an outlet side of the compressor 120 to the main line 10, the seventh and eighth auxiliary lines 10g and 10h connect an inlet side and an outlet side of the ice thermal storage system 700 to the main line 10, and the ninth and tenth auxiliary lines 10i and 10j connect an inlet side and an outlet side of the pump 110 to the main line 10. Additionally, a first bypass line 20a for avoiding each of the first expansion valve 610a and the first capillary tube 620a provided in the first auxiliary line 10a may be provided, and a second bypass line 20b for avoiding each of the second expansion valve 610b and the second capillary tube 620b provided in the second auxiliary line 10b may be provided. Similarly, a third bypass line 20c for avoiding each of the third expansion valve 610c and the third capillary tube 620c provided in the third auxiliary line 10c may be provided, and a fourth bypass line 20d for avoiding each of the fourth expansion valve 610d and the fourth capillary tube 620d provided in the fourth auxiliary line 10d may be provided.
As described above, since the heat load system according to the present embodiment includes the first to tenth auxiliary lines 10a to 10j and the first to fourth bypass lines 20a to 20d, a working fluid may selectively pass through at least one of the heat dissipation means 400, the heat supply means 500, the adjustment means 600 (the first to fourth expansion valves 610a to 610d and the first to fourth capillary tubes 620a to 602d), the ice thermal storage system 700, the pressurized means 100, the pump 110, and the compressor 120. That is, the working fluid may selectively pass through at least one of the heat dissipation means 400, the heat supply means 500, the adjustment means 600 (the first to fourth expansion valves 610a to 610d and the first to fourth capillary tubes 620a to 602d), the ice thermal storage system 700, and the pressurized means 100 (the pump 110 and the compressor 120) as needed, and may avoid the rest. As a result, the working fluid may selectively pass through only certain configurations.
A working fluid receives cold-heat from a first medium while passing through the first heat exchanger 200, thereby decreasing in temperature (the temperature of the first medium increases). At this time, the enthalpy decreases in the P-h line diagram and passes through a saturated liquid line (1 in
In the above-described process, when the amount of cold-heat of a first medium is greater than the amount of heat of a second medium by a first predetermined value, the ice thermal storage system 700 absorbs (ice thermal storage) cold-heat from a working fluid to balance the amount of cold-heat of the first medium and the amount of heat of the second medium. That is, when the amount of cold-heat of the first medium is greater than the amount of heat of the second medium by a relatively small amount (a first predetermined value), the ice thermal storage system 700 may absorb cold-heat, thereby balancing the amount of cold-heat of the first medium and the amount of heat of the second medium.
The working fluid receives cold-heat from the first medium while passing through the first heat exchanger 200, thereby decreasing in temperature (the temperature of the first medium increases). At this time, enthalpy decreases in the P-h line diagram and moves in a direction of a saturated liquid line (1 in
Thereafter, the working fluid receives heat from a second medium while passing through the second heat exchanger 300, thereby increasing in temperature (the temperature of the second medium decreases). At this time, enthalpy increases in the P-h line diagram and passes through a saturated liquid line (3 in
In the above-described process, when the amount of cold-heat of the first medium is greater than the amount of heat of a second medium by a first predetermined value, the heat supply means 500 supplies heat to a working fluid to balance the amount of cold-heat of the first medium and the amount of heat of the second medium (for example, when an ice thermal storage capacity of the ice thermal storage system 700 reaches saturation, the heat supply means 500 may supply heat to the working fluid). That is, when the amount of cold-heat of the first medium is greater than the amount of heat of the second medium by a relatively small amount (the first predetermined value), the heat supply means 500 supplies heat to the cold-heat of the first medium to balance the cold-heat of the first medium and the heat of the second medium.
The working fluid receives heat while passing through the heater 800, thereby increasing in temperature. At this time, enthalpy increases in the P-h line diagram (1 in
Thereafter, the working fluid decreases in pressure while passing through the expansion valves 610a and 610b of the adjustment means 600. At this time, the pressure decreases in the P-h line diagram (5 in
In the above-described process, when the amount of cold-heat of a first medium is greater than the amount of heat of a second medium by a second predetermined value (the second predetermined value is greater than the first predetermined value), the heater 800 supplies heat to a working fluid to balance the amount of cold-heat of the first medium and the amount of heat of the second medium. That is, when the amount of cold-heat of the first medium is greater than the amount of heat of the second medium by a relatively large amount (the second predetermined value), the heater 800 supplies heat to balance the amount of cold-heat of the first medium and the amount of heat of the second medium.
A working fluid receives heat while passing through the heater 800, thereby increasing in temperature. At this time, enthalpy increases in the P-h line diagram (1 in
In the above-described process, when the amount of cold-heat of a first medium is greater than the amount of heat of a second medium by a third predetermined value (the third predetermined value is greater than the second predetermined value), not only the heater 800 supplies heat to a working fluid but also the heat supply means 500 supplies heat to the working fluid to balance the amount of cold-heat of the first medium and the amount of heat of the second medium. That is, when the amount of cold-heat of the first medium is greater than the amount of heat of the second medium by a relatively large amount (the third predetermined value), the heater 800 and the heat supply means 500 supply heat, and thus, the amount of cold-heat of the first medium and the amount of heat of the second medium may be balanced.
A working fluid receives heat while passing through the heater 800, thereby increasing in temperature. At this time, enthalpy increases in the P-h line diagram (1 in
Thereafter, the working fluid decreases in pressure while passing through the expansion valve 610d of the adjustment means 600. At this time, the pressure decreases in the P-h line diagram (7 in
In the above-described process, when the amount of cold-heat of a first medium is greater than the amount of heat of a second medium by a fourth predetermined value (the fourth predetermined value is greater than the third predetermined value), the heater 800 supplies heat to a working fluid, the heat supply means 500 also supplies heat to the working fluid, the ice thermal storage system 700 absorbs cold-heat, and thus, the amount of cold-heat of the first medium and the amount of heat of the second medium are balanced. That is, when the amount of cold-heat of the first medium is greater than the amount of heat of the second medium by a relatively very large amount (the fourth predetermined value), the heater 800 and the heat supply means 500 supply heat, and the ice thermal storage system 700 absorbs cold-heat, and thus, the amount of cold-heat of the first medium and the amount of heat of the second medium may be balanced.
A working fluid receives cold-heat from the first medium while passing through the first heat exchanger 200, thereby decreasing in temperature (the temperature of the first medium increases). At this time, enthalpy decreases in the P-h line diagram and moves in a direction of a saturated liquid line (1 in
In the above-described process, when the amount of heat of a second medium is greater than the amount of cold-heat of a first medium by a fifth predetermined value, the ice thermal storage system 700 supplies cold-heat to a working fluid to balance the amount of cold-heat of the first medium and the amount of heat of the second medium. That is, when the amount of heat of the second medium is greater than the amount of cold-heat of the first medium by a relatively small amount (the fifth predetermined value), the ice thermal storage system 700 supplies cold-heat, and thus, the amount of cold-heat of the first medium and the amount of heat of the second medium may be balanced.
A working fluid receives cold-heat from a first medium while passing through the first heat exchanger 200, thereby decreasing in temperature (the temperature of the first medium increases). At this time, enthalpy decreases in the P-h line diagram and moves in a direction of a saturated liquid line (1 in
In the above-described process, when the amount of heat of a second medium is greater than the amount of cold-heat of a first medium by a fifth predetermined value, the heat dissipation means 400 dissipates heat (in this case, heat may also be dissipated through the capillary tube 620b) to balance the amount of cold-heat of the first medium and the amount of heat of the second medium. That is, when the amount of heat of the second medium is greater than the amount of cold-heat of the first medium by a relatively small amount (the fifth predetermined value), the heat dissipation means 400 dissipates heat, thereby balancing the amount of cold-heat of the first medium and the amount of heat of the second medium.
A working fluid receives cold-heat from a first medium while passing through the first heat exchanger 200, thereby decreasing in temperature (the temperature of the first medium increases). At this time, enthalpy decreases in the P-h line diagram and moves in a direction of a saturated liquid line (1 in
In the above-described process, when the amount of heat of a second medium is greater than the amount of cold-heat of a first medium by a sixth predetermined value (the sixth predetermined value is greater than the fifth predetermined value), the ice thermal storage system 700 supplies cold-heat, the heat dissipation means (400) dissipates heat through the capillary tube 620b, and thus, the amount of cold heat of the first medium and the amount of heat of the second medium are balanced. That is, when the amount of heat of the second medium is greater than the amount of cold-heat of the first medium by a relatively large amount (the sixth predetermined value), the ice thermal storage system 700 supplies cold-heat, and the heat dissipation means 400 and the capillary tube 620b dissipate heat, and thereby, the amount of cold-heat of the first medium and the amount of heat of the second medium may be balanced.
In addition, although it is described that a working fluid increases in pressure while passing through the pump 110 as the pressurized means 100, the present invention is not limited thereto, and the working fluid may also increase in pressure while passing through the compressor 120 as the pressurized means 100. For example, when the working fluid is in a liquid state, the working fluid may pass through the pump 110, and as described below, when the working fluid is in a gaseous state, the working fluid may pass through the compressor 120.
The working fluid receives cold-heat from a first medium while passing through the first heat exchanger 200, thereby decreasing in temperature (the temperature of the first medium increases). At this time, enthalpy decreases in the P-h line diagram and moves in a direction of a saturated liquid line (1 in
In the above-described process, when the amount of cold-heat of a first medium is greater than the amount of heat of a second medium, the compressor 120 supplies heat to a working fluid to balance the amount of cold-heat of the first medium and the amount of heat of the second medium. In this way, since the temperature and enthalpy may be increased through the compressor 120, when heat of the working fluid is exchanged in the first heat exchanger 200, the working fluid may be at a higher temperature condition, compared to the previous cases, and when heat of the working fluid is exchanged in the heat exchanger 300, the working fluid may be at a lower temperature condition compared to the previous cases.
A working fluid receives cold-heat from a first medium while passing through the first heat exchanger 200, thereby decreasing in temperature (the temperature of the first medium increases). At this time, enthalpy decreases in the P-h line diagram and moves in a direction of a saturated liquid line (1 in
In the above-described process, when the amount of cold-heat of a first medium is greater than the amount of heat of a second medium, the heat supply means 300 and the compressor 120 supply heat to a working fluid to balance the amount of cold-heat of the first medium and the amount of heat of the second medium. In order for the working fluid to absorb heat while passing through the heat supply means 500, the working fluid has to be sufficiently cooled while passing through the first heat exchanger 200, but when the working fluid is not sufficiently cooled, the working fluid passes through the capillary tube (620d, or the expansion valve) to be decreased in pressure and temperature, thereby absorbing heat in an isothermal process.
A working fluid receives cold-heat from a first medium while passing through the first heat exchanger 200, thereby decreasing in temperature (the temperature of the first medium increases). At this time, enthalpy decreases in the P-h line diagram and passes through a saturated liquid line and a phase change is made (1 in
In the above-described process, when the amount of cold-heat of a first medium is greater than the amount of heat of a second medium, the heat supply means 500 and the compressor 120 supply heat to a working fluid to balance the amount of cold-heat of the first medium and the amount of heat of the second medium. When the working fluid is cooled while passing through the first heat exchanger 200 and phase-changed to a liquid, the pressure is decreased by the expansion valve 610d, an the evaporative temperature of the working fluid is decreased in a two-phase state, efficiency is increased by an isothermal process, and the additional heat may be absorbed.
A working fluid receives cold-heat from a first medium while passing through the first heat exchanger 200, thereby decreasing in temperature (the temperature of the first medium increases). At this time, enthalpy decreases in the P-h line diagram and moves in a direction of a saturated liquid line (1 in
At this time, the enthalpy increases in the P-h line diagram and moves in a direction of a saturated steam line (4 in
In the above-described process, when cold-heat of a first medium and heat of a second medium are the same, a balance of the amount of cold-heat of the first medium and the amount of heat of the second medium is maintained by using the heat dissipation means 400, the capillary tube 620a, the compressor 120, and so on. In order for the working fluid to sufficiently absorb heat in the second heat exchanger 300, the working fluid may decrease in temperature while passing through the first heat exchanger 200 and then passing through the heat dissipation means 400 and may decrease in temperature and pressure while passing through the capillary tube 620a.
A working fluid receives cold-heat from a first medium while passing through the first heat exchanger 200, thereby decreasing in temperature (the temperature of the first medium increases). At this time, enthalpy decreases in the P-h line diagram and moves in a direction of a saturated liquid line (1 in
In the above-described process, when the amount of cold-heat of a first medium and the amount of heat of a second medium are the same, a balance of the amount of cold-heat of the first medium and the amount of heat of the second medium is maintained by using the heat dissipation means 400, the compressor 120, and so on. In order for the working fluid to sufficiently absorb heat in the second heat exchanger 300, the working fluid may decrease in temperature while passing through the first heat exchanger 200 and then passing through the heat dissipation means 400 so as to be cooled in a liquid state, and then may decrease in only pressure without a decrease in temperature while passing through the expansion valve 610a.
Meanwhile, the heat load control system according to the present invention has an advantage in that stable heat exchange is made because of the operation in a region adjacent to a saturated liquid line and a saturated steam line on a P-h line diagram as described above.
As illustrated in
As illustrated in
As a result, there is a need to absorb a difference in the amount of heat between the cooling load of the first medium (liquefied natural gas) that may be predicted and the load of the second medium (waste heat of a data center, waste heat of a shopping mall, or so on) that may not be predicted, and the heat load control system according to the embodiment of the present invention may absorb the difference in the amount of heat described above by using, for example, the ice thermal storage system 700.
Although the present invention is described in detail through specific examples, this is for the purpose of describing the present invention in detail, and the present invention is not limited thereto, and it is apparent that modifications or improvements may be made by those skilled in the art within the technical idea of the present invention.
All simple modifications or changes of the present invention belong to the scope of the present invention, and the specific protection scope of the present invention will be made clear by the appended claims.
Number | Date | Country | Kind |
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10-2019-0158464 | Dec 2019 | KR | national |
10-2020-0065796 | Jun 2020 | KR | national |
Filing Document | Filing Date | Country | Kind |
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PCT/KR2020/017128 | 11/27/2020 | WO |