KR20110032051A - Absorption refrigeration using engine's waste heat - Google Patents

Abstract

PURPOSE: An absorptive freezer using the waste heat of the engine is provided to reduce cost by the utilizing of a room-temperature compressor in the re-liquefying process of gas and to utilize environment-friendly refrigerant. CONSTITUTION: An absorptive freezer(100) using the waste heat of the engine comprises a regenerator(110), a condenser(120), an evaporator(130) and an absorber(140). The regenerator uses the engine waste-heat(170) as a heat source and heats the mixture(142) of an absorbent(141) and refrigerant(131) to separate the refrigerant from the absorbent. The condenser condenses vapor refrigerant, which has been separated by the regenerator, using the cooling water(151). The evaporator evaporates the condensed refrigerant at a low pressure and absorbs the heat energy from the outside. The absorber absorbs the evaporated refrigerant using the absorbent and generates the mixture.

Description

Absorption Refrigeration using Engine's Waste Heat

The present invention relates to an absorption chiller utilizing waste heat of an engine provided in a drive body using an engine as a heat source of an absorption chiller.

1 is a structural diagram showing a schematic configuration of a conventional absorption chiller.

Referring to FIG. 1, a conventional general absorption type refrigerator 10 uses a low temperature heat source generated by evaporation of a refrigerant in an evaporator 13 for various cooling needs such as cooling a building. District heating heat or heat generated by burning gas was used. In addition, in order to cool the high temperature heat generated in the absorber 14 and the condenser 12, the cooling tower 15 is used to circulate the cooling water.

FIG. 2 is a flowchart illustrating a schematic configuration of a gas reliquefaction process in a conventional LPG carrier.

Referring to FIG. 2, in the reliquefaction process of liquefied petroleum gas (LPG), the low temperature low pressure evaporation gas generated in the low temperature low pressure cargo hold 20 is compressed through a low temperature compressor 21 to be a normal temperature medium pressure evaporation gas. The boil-off gas cooled in the economizer 22 is compressed again in the low temperature compressor 21 and liquefied through the condenser 23. The liquefied hot boil off gas is cooled while passing back through the economizer 22. The cooling source of the economizer 22 is obtained by liquefying a part of the room temperature high pressure liquefied cargo through the cooling flash valve 24.

Looking at the conventional problem,

First, the conventional absorption chiller 10 shown in FIG. 1 has a disadvantage of consuming extra energy because the heat source of the regenerator 11 is obtained by a separate combustion device.

Second, in the case of the mechanical refrigerator used in the prior art to produce electricity with a diesel generator that consumes diesel oil without directly using the waste heat of the engine, it must be cooled by using electrical energy. To this end, diesel oil needs to be loaded on a ship, and there is a problem in that it needs to be consumed for electricity production.

Third, in the case of utilizing engine waste heat in a ship, a turbine was driven by steam generated by using exhaust gas or exhaust gas of the engine instead of directly using the engine waste heat. In this case, the equipment for utilizing the engine waste heat is expensive, the efficiency is reduced because only the exhaust gas of the engine of the various waste heat of the engine is utilized, there is a problem that the energy efficiency during the energy conversion process.

Fourth, in the conventional reliquefaction process of the liquefied gas, the evaporated gas is used as a fuel of the engine or liquefied by obtaining a compressor power by using electrical energy or the like. In this case, a low cost compressor must be used, which is a costly disadvantage. In addition, there is a problem in that the reliquefaction efficiency of the liquefied gas is low because a part of the liquefied gas cooled as a cooling source of the economizer is used to use an economizer for cooling the low temperature compressor.

Therefore, by effectively utilizing the various waste heat of the engine to drive the absorption chiller without extra energy consumption, when utilizing the re-liquefaction of the gas loaded on the vessel, using a relatively inexpensive room temperature compressor, utilization efficiency of waste heat and gas It is urgent to develop an absorption type refrigerator having high reliquefaction efficiency.

The present invention seeks to provide an absorption chiller that does not require any energy or equipment by utilizing waste heat of the engine for heating the mixture of the absorbent and the refrigerant and driving the regenerator.

The present invention is to provide an absorption chiller that can utilize a room temperature compressor by converting to a suitable temperature before compressing the cooling object.

The present invention seeks to provide an eco-friendly absorption chiller utilizing a natural refrigerant such as water (H 2 O) or ammonia (NH 3).

The present invention provides an absorption chiller using engine waste heat provided in a driving body using an engine as a drive source, wherein at least one engine waste heat 170 is used as a heat source, and a mixture in which an absorbent 141 and a refrigerant 131 are mixed ( A regenerator 110 that heats 142 to separate and extract the refrigerant 131 and the absorbent 141; A condenser (120) for condensing the refrigerant (131) in the gas phase separated from the regenerator (110) using cooling water (151); An evaporator (130) for absorbing thermal energy from the outside by evaporating the refrigerant (131) of the liquid phase condensed in the condenser (120) at low pressure; The coolant 151 absorbs the refrigerant 131 evaporated from the evaporator 130 into the absorbent 141 to generate the mixture 142, and maintains a temperature suitable for the reaction of generating the mixture 142. Absorber 140 for cooling by using to produce the mixture 142; It is made, including, the evaporator 130 is characterized in that to absorb the heat energy from the cooling object 160 passing through the periphery of the evaporator (130).

In the present invention, the engine waste heat 170 is any one selected from the first engine waste heat 171 or the second engine waste heat 172, and the first engine waste heat 171 is the exhaust gas of the engine or the exhaust gas of the engine. Heat generated from any one selected from steam heated using the second engine waste heat 172 is characterized in that the heat generated from the cooling water used for cooling the engine.

The condenser 120 and the condenser 120 and the cooling object 160 passing through the evaporator 130 and the cooling object 160 passing through the evaporator 130 are exchanged with each other. A first heat exchanger 161 provided on the flow path between the evaporators 130; The compressor 162 is provided on a path through which the cooling object 160 passed through the first heat exchanger 161 flows in order to compress the cooling object 160 heat exchanged in the first heat exchanger 161. ; Including, but the cooling object 160 is compressed in the compressor 162 is transferred to the periphery of the evaporator 130 is characterized in that the cooling after transferring the heat energy to the evaporator (130).

In the present invention, the cooling object 160 moving through the compressor 162 to the periphery of the evaporator 130 and the mixture 142 moving from the absorber 140 to the regenerator 110 exchange each other. It characterized in that it comprises a second heat exchanger 163 provided on the flow path between the absorber 140 and the regenerator 110 as possible.

According to the present invention, the absorber 141 moving from the regenerator 110 to the absorber 140 and the mixture 142 moving from the absorber 140 to the regenerator 110 exchange heat with each other. 140 and a third heat exchanger 143 provided on the flow path between the regenerator 110, wherein the mixture 142 moving from the absorber 140 to the regenerator 110 is the third heat exchanger. After passing through the unit 143, it is characterized in that flowing into the second heat exchanger (163).

The present invention uses the second engine waste heat 172 as a heat source between the absorber 140 and the regenerator 110 to heat the mixture 142 moving from the absorber 140 to the regenerator 110. And a fourth heat exchanger 144 provided on the flow path, wherein the mixture 142 moving from the absorber 140 to the regenerator 110 passes through the second heat exchanger 163. The fourth heat exchanger 144 is characterized in that it is introduced.

According to an embodiment of the present invention, a first auxiliary cooler may be disposed on a flow path between the second heat exchanger 163 and the evaporator 130 to assist cooling of the cooling object 160 that has passed through the second heat exchanger 163. 164 is provided.

The present invention is characterized in that the absorbent 141 and the refrigerant 131 use water (H 2 O) as the absorbent 141 and ammonia (NH 3) as the refrigerant 131.

The present invention is characterized in that the absorbent 141 and the refrigerant 131 use lithium bromide (LiBr) as the absorbent 141 and water (H 2 O) as the refrigerant 131.

The cooling object 160 is characterized in that the evaporated gas evaporated from any one selected from liquefied petroleum gas (LPG), liquefied natural gas (LNG), carbon dioxide (CO2).

The present invention is characterized in that the cooling water 151 is sea water.

The fifth heat exchanger 152 uses the thermal energy of the cooling water 151 used for cooling in the absorber 140 and the condenser 120 in the cooling line 150 through which the cooling water 151 flows. ) Is characterized in that it is provided.

According to the present invention, when the cooling object 160 is liquefied natural gas (LNG), the cooling object 160 passes through the periphery of the evaporator 130 to assist cooling of the cooling object 160 that has passed through the periphery of the evaporator 130. A second auxiliary cooler 165 is provided in the flow path of the cooling object 160.

Absorption type refrigerator using engine waste heat according to the present invention,

First, it utilizes a variety of waste heat of the engine, it is advantageous in terms of energy utilization and economical because no separate equipment or energy is required.

Second, there is an advantage that can use a relatively inexpensive room temperature compressor without using a low temperature compressor in the gas reliquefaction process.

Third, it is eco-friendly because it can utilize a nature-friendly refrigerant.

Fourth, the cooling water used in the condenser and the absorber can be recycled as a water source for living water and heating of the ship, it is possible to use energy efficiently.

Fifth, it is economical because sea water can be utilized as cooling water. However, when the high temperature medium is cooled with sea water, scale may occur on the heat transfer surface due to salts caused by sea water. Therefore, fresh water may be used to cool the medium at a high temperature, and seawater may be used to cool the fresh water again.

Generally, the absorption chiller may be configured by connecting an evaporator in which the refrigerant is evaporated, an absorber in which the refrigerant is absorbed by the absorbent, a regenerator for heating the absorbed refrigerant to regenerate the refrigerant, and a condenser for condensing the refrigerant. The absorption chiller is provided with a cooling device to remove heat generated when the absorbent absorbs the refrigerant in the absorber and to condense the evaporated refrigerant.

In addition, hydrocarbon gas, including liquefied natural gas (LNG) and liquefied petroleum gas (LPG) is generally transported by using a bulk gas carrier (Bulk Gas Carrier). In this case, in order to avoid high pressure, it is transported at atmospheric pressure around 1 atm, and the temperature must be kept at a low temperature for this purpose. Liquefied natural gas (LNG) is stored at -160 ° C and propane liquefied petroleum gas (LPG) is stored at -45 ° C. Therefore, it is necessary to maintain a very low temperature condition lower than room temperature, even if the thermal insulation equipment will cause heat penetration from the outside. The penetration of heat causes evaporation of the liquefied cargo gas, which is called a boil-off gas. The boil-off gas is used as fuel of a ship engine or liquefied and stored by a reliquefaction facility.

Hereinafter, an embodiment of the present invention will be described in detail with reference to the accompanying drawings. 3 is a structural diagram showing a schematic configuration of an absorption chiller using engine waste heat according to the present invention.

Referring to FIG. 3, the absorption chiller 100 may include a regenerator 110, a condenser 120, an evaporator 130, and an absorber 140. Hereinafter, the first description will be made according to the flow of the refrigerant 131 in the absorption chiller 100, and then the description will be made according to the flow of the cooling object 160.

The heat source of the absorption chiller 100 is the engine waste heat 170 provided in the drive body using the engine as a drive source. The driving body may be various driving bodies equipped with an engine such as a ship or an automobile. The engine waste heat 170 may be divided into a first engine waste heat 171 and a second engine waste heat 172. The first engine waste heat 171 is heat generated from steam heated using the exhaust gas heat of the engine or the exhaust gas heat of the engine. The second engine waste heat 172 is heat generated from the high temperature cooling water used for cooling the engine. The engine waste heat 170 may include various types of heat generated when driving an engine including the heat described above.

Referring to FIG. 3, the regenerator 110 may use at least one engine waste heat 170 as a heat source. The regenerator 110 serves to separate and extract the refrigerant 131 and the absorbent 141 by heating the mixture 142 in which the absorbent 141 and the refrigerant 131 are mixed. That is, the regenerator 110 absorbs the coolant 131 and heats the mixture 142 in which the concentration is diminished and the absorption ability is reduced, thereby making the absorbent 141 a thick absorbent solution. The regenerator 110 may be provided with an internal heat exchanger (not given a number) for reheating the mixture 142 by utilizing the engine waste heat 170 as a heat source. Pipes may be connected to the regenerator internal heat exchanger (not shown) so that hot water or hot gas or steam may flow in and out according to the type of the engine waste heat 170. A refrigerant pipe (not shown) may be connected to an upper portion of the regenerator 110 to allow the refrigerant 131 separated by heating the mixture 142 to flow. The refrigerant pipe (not shown) The refrigerant 131 separated through the condenser is moved to the condenser 120. The regenerator 110 may be provided with an absorbent pipe (not given a number) for transferring the separated absorbent 141 to the absorbent 141 by heating the mixture 142. In addition, a mixture pipe (not given a number) may be connected to the regenerator 110 so that the mixture 142 transferred from the absorber 140 may be introduced.

Referring to FIG. 3, the condenser 120 is a device for condensing the refrigerant 131 in the gas state separated by heating from the regenerator 110 using the cooling water 151. The refrigerant 131 is different depending on the type of refrigerant, but is separated from the regenerator by heating in the regenerator 110 and is generally in a state of high temperature and high pressure. A lower end of the condenser 120 may be provided with a refrigerant pipe (not shown) to flow the refrigerant 131 in the condensed liquid state to the evaporator 130. In addition, the inside of the condenser 120 may be provided with a heat exchanger (not shown) in the condenser so that the cooling water 151 flows. A description of the flow of the cooling water 151 in the condenser 120 will be described later. In addition, since the condenser 120 is the same as the condenser in the general absorption chiller, it will be omitted.

Referring to FIG. 3, the evaporator 130 is a device that absorbs thermal energy from the outside by evaporating the refrigerant 131 in a liquid state condensed in the condenser 120 at low pressure. The evaporator 130 may be provided in a single body together with the absorber 140 according to a design. The evaporator 130 is preferably provided with an evaporator internal heat exchanger (not shown). The evaporator 130 maintains a low pressure to induce the refrigerant 131 to evaporate at a relatively low temperature. As the refrigerant 131 evaporates, heat energy is absorbed from the cooling object 160 passing through the evaporator 130, thereby cooling the cooling object 160. The heat exchanger (not shown) inside the evaporator continuously cools the refrigerant 131 in the liquid state that has passed through the condenser 120 to cool, and the refrigerant 131 in the evaporated gas state has the Transferred to absorber 140. The cooling object 160 will be described later. In addition, the details of the evaporator 130 is omitted because it is the same as the evaporator in a general absorption chiller.

Referring to FIG. 3, the absorber 140 absorbs the refrigerant 131 evaporated from the evaporator 130 into the absorbent 141 to generate the mixture 142. Since the absorbent 141 absorbs the refrigerant 131 in general, it is an exothermic process, so that the absorbent 141 needs to maintain a proper temperature so as to continuously absorb the refrigerant 131. To this end, the absorber 140 is preferably provided with an absorber internal heat exchanger (not shown). The heat exchanger (not shown in the drawing) of the absorber serves to offset heat generated when the absorbent 141 absorbs the refrigerant 131 using the cooling water 151. Thus, the absorber 140 cools using the cooling water 151 to generate the mixture 142 to maintain a temperature suitable for the reaction of formation of the mixture 142. A description of the flow of the cooling water 151 flowing in the absorber 140 will be described later. An absorbent pipe (not given a number) may be connected to an upper portion of the absorber 140 to allow a high concentration of the absorbent 141 solution to flow from the regenerator 110. In the lower part of the absorber 140 to absorb the refrigerant 131 evaporated in a gaseous state to flow the mixture 142, the absorbent solution of which the concentration is diluted, to the regenerator 110 (not shown) Imparted) is preferably connected. The mixture pipe (not shown) may include a pump (not shown) for transferring the mixture 142 to the regenerator 110 according to design. In addition, the contents of the absorber 140 are the same as those of the absorber in a general absorption chiller and thus will be omitted.

Referring to FIG. 3, the absorption chiller 100 may optionally include a first heat exchanger 161 and a compressor 162. The first heat exchanger 161 mutually heat-exchanges the refrigerant 131 moving from the condenser 120 to the evaporator 130 and the cooling object 160 which is transferred to pass through the periphery of the evaporator 130. Device. The first heat exchanger 161 is preferably provided on the flow path between the condenser 120 and the evaporator 130 in the flow path of the refrigerant 131. Hereinafter, a case where the cooling object 160 is a low temperature low pressure evaporated gas (Boil-off Gas) will be described. Boil-off gas of low temperature and low pressure must pass through the compressor 162 for the reliquefaction process. In this case, when the low temperature compressor is used as in the prior art, there is a problem in that the cost is great. In the present invention, when the refrigerant 131 in the liquid state passing through the condenser 120 and the cooling object 160 are mutually heat exchanged in the first heat exchanger 161, a low-temperature low-pressure evaporation gas (Boil-off) The cooling object 160, which is a gas, may absorb thermal energy and become a boil-off gas at room temperature and low pressure. Therefore, there is an advantage that can use a room temperature compressor rather than an expensive low temperature compressor. At the same time, since the refrigerant 131 that generates heat energy through heat exchange in the first heat exchanger 161 is lowered to a lower temperature and flows into the evaporator 130, the heat exchanger inside the evaporator (not shown). It also has the advantage of reducing the energy and time required for the cooling process.

Referring to FIG. 3, the compressor 162 may include the cooling object 160 passing through the first heat exchanger 161 to compress the cooling object 160 heat exchanged in the first heat exchanger 161. It is preferable to be provided in the flow path. As described above, the compressor 162 may use a room temperature compressor having a relatively low cost. When the cooling object 160 is an evaporation gas, a low temperature boil-off gas is introduced into the compressor 162, and the high temperature and high pressure evaporation gas is compressed by the compressor 162. -off gas) and released. The cooling object 160 compressed by the compressor 162 is transferred to the periphery of the evaporator 130 to transfer heat energy to the evaporator 130 and then cooled. The heat exchange process between the refrigerant 131 and the cooling object 160 in the evaporator 130 has already been described above.

Referring to FIG. 3, the absorption chiller 100 may optionally include a second heat exchanger 163. The second heat exchanger 163 passes through the compressor 162 and moves to the periphery of the evaporator 130 and the mixture moving from the absorber 140 to the regenerator 110. 142 is a device for mutual heat exchange. Thus, when viewed from the flow path of the refrigerant 131, the second heat exchanger 163 is on the flow path of the mixture 142 including the refrigerant 131 between the absorber 140 and the regenerator 110. It is preferable to be provided in. When viewed from the flow path of the cooling object 160 is preferably provided on the flow path to move through the compressor 162 to the periphery of the evaporator (130). When the cooling object 160 is an evaporating gas, the high temperature and high pressure boil-off gas passing through the compressor 162 is primarily cooled while passing through the second heat exchanger 163. In order to liquefy the cooling object 160, the evaporator 130 preferably has a low-temperature evaporative gas (Boil-off Gas) flowed in, so that the cooling object 160 is cooled to a room temperature state.

Referring to FIG. 3, when the cooling object 160 is not sufficiently cooled to room temperature by heat exchange in the second heat exchanger 163, the absorption chiller 100 includes a first auxiliary cooler 164 according to a design. It may be provided. That is, the first auxiliary cooler 164 may be provided to assist cooling of the cooling object 160 that has passed through the second heat exchanger 163. The first auxiliary cooler 164 is preferably provided on the flow path of the cooling object 160 between the second heat exchanger 163 and the evaporator 130. When the cooling object 160 is an evaporation gas, the cooling object 160 passes through the first auxiliary cooler 164 to become a boil-off gas at room temperature and high pressure and flows into the evaporator 130. Will be.

Referring to FIG. 3, the second heat exchanger 163 heat exchanges the mixture 142 in which the refrigerant 131 and the absorbent 141 are mixed in the absorber 140. Since the mixture 142 has a relatively low temperature, the mixture 142 may be primarily heated while exchanging heat with the high temperature cooling object 160 passing through the second heat exchanger 163.

Referring to FIG. 3, the absorption chiller 100 may optionally include a fourth heat exchanger 144. The fourth heat exchanger 144 is a device for heating the mixture 142 moving through the second heat exchanger 163 to the regenerator 110 using the second engine waste heat 172. Accordingly, the fourth heat exchanger 144 is provided on a path through which the mixture 142 flows between the absorber 140 and the regenerator 110, and the mixture 142 is connected to the second heat exchanger 163. After passing through), it is preferable to flow into the fourth heat exchanger (144). In terms of thermal efficiency, it is advantageous to utilize a low temperature heat source from a high temperature heat source in order to heat the mixture 142. In general, the second engine waste heat 172 used as a heat source of the fourth heat exchanger 144 is relatively hotter than the cooling object 160 passing around the second heat exchanger 163. Therefore, it is preferable in terms of thermal efficiency that the mixture 142 is designed to be heated secondly in the fourth heat exchanger 144 after being primarily heated in the second heat exchanger 163. As described above, the second engine waste heat 172 includes various types of heat generated in driving the engine, including heat generated from the high temperature cooling water used for cooling the engine.

Referring to FIG. 3, the absorption chiller 100 may optionally include a third heat exchanger 143. The third heat exchanger 143 separates the absorbent 141 separated from the regenerator 110 and returned to the absorbent 141 and the mixture 142 transferred from the absorber 140 to the regenerator 110. It is a device for mutual heat exchange. That is, the heat energy contained in the absorbent 141 separated by heating in the regenerator 110 is transferred to the mixture 142 mixed in the absorber 140 to heat the mixture 142. Therefore, the third heat exchanger 143 is preferably provided on the flow path of the absorbent 141 and the mixture 142 between the absorber 140 and the regenerator 110. However, in view of the thermal efficiency as described above, the absorbent 141 passing through the third heat exchanger 143 is relatively high temperature than the cooling object 160 passing through the second heat exchanger 163. Since the mixture 142, which is transferred from the absorber 140 to the regenerator 110, is preliminarily heated in the third heat exchanger 143, the mixture 142 may be transferred to the second heat exchanger 163. It is preferred to be introduced and heated primarily.

Of course, the refrigerant 131 and the absorbent 141 used in the absorption refrigerator 100 may vary. In addition, the refrigerant 131 and the absorbent 141 may vary according to the type of the cooling object 160. However, when water (H20) is used as the absorbent 141 in consideration of environmentally friendly elements, ammonia (NH3) may be used as the refrigerant 131. In addition, when lithium bromide (LiBr) is used as the absorbent 141, water (H 2 O) may be used as the refrigerant 131.

In the present invention, the absorption chiller 100 using waste heat of the engine can be utilized in various fields, of course. Examples of the absorption chiller 100 may be utilized in various ways, such as cooling of liquefied carbon dioxide, refrigeration vessels for ships, reliquefaction of gas in cargo gas carriers, and air conditioning. Hereinafter, an embodiment in which the cooling object 160 is a boil-off gas evaporated from any one selected from liquefied petroleum gas (LPG), liquefied natural gas (LNG), and carbon dioxide (CO2) will be described. Let's do it.

As described above, there is a need for equipment for reliquefaction of Boil-off Gas in large vessels carrying cargo gas. When the absorption chiller 100 is applied thereto, the cooling object 160 is an evaporated gas evaporated from any one selected from liquefied petroleum gas (LPG), liquefied natural gas (LNG), and carbon dioxide (CO2). -off Gas). However, as described above, the storage temperature of the liquefied petroleum gas (LPG) and the liquefied natural gas (LNG) is different, and when the cooling object 160 is a liquefied natural gas (LNG), a lower temperature should be maintained.

Referring to FIG. 3, the absorption chiller 100 may optionally include a second auxiliary cooler 165. The second auxiliary cooler 165 flows the cooling object 160 through the periphery of the evaporator 130 to assist cooling of the cooling object 160 through the periphery of the evaporator 130. It is preferred to be provided on the path. In particular, as described above, the cooling object 160 should be liquefied in the evaporator 130 and transferred to the cooling object tank 166 to be accommodated. When the cooling object 160 is a liquefied natural gas (LNG), a case where the cooling object 160 is not sufficiently liquefied even though the cooling process is performed in the evaporator 130 may occur. The cooling object 160 may be further cooled to liquefy.

Referring to FIG. 3, the cooling water 151 for cooling flows in the condenser 120 and the absorber 140. Looking at the cooling line 150 in which the cooling water 151 flows, the cooling water 151 accommodated in the cooling water tank 155 is a heat exchanger inside each condenser provided in the condenser 120 and the absorber 140. (Not shown) and to the heat exchanger inside the absorber (not shown). The cooling water 151 utilized for cooling in the condenser internal heat exchanger (not shown) and the absorber internal heat exchanger (not shown) absorbs thermal energy. The fifth heat exchanger 152 may be provided to utilize the thermal energy of the cooling water 151.

Referring to FIG. 3, the absorption chiller 100 may optionally include the fifth heat exchanger 152. The fifth heat exchanger 152 is provided in the cooling line 150 through which the cooling water 151 flows, and used for cooling in the absorber 140 and the condenser 120 and absorbing thermal energy ( 151 may be provided to use the thermal energy. The heat energy obtained from the fifth heat exchanger 152 may be used as heating heat for heating. In addition, when living organisms ride on a driving body that uses an engine such as a ship as a driving source, it can be utilized as living water (hot water) for them. In addition, an embodiment utilized to heat a cargo mounted on a ship or the like may also be considered. In addition, the heat energy obtained from the fifth heat exchanger 152 may be used in various embodiments.

When the absorption chiller 100 is utilized in a vessel, the cooling water 151 may be sea water. When the sea water (sea water) is used as the cooling water 151, there is an advantage that can be utilized without the need to load a separate cooling water. However, when the high temperature medium is cooled with sea water, scale may occur on the heat transfer surface due to salts caused by sea water. Therefore, it is possible to consider a method of using fresh water for cooling the medium at high temperature and cooling the fresh water back to sea water. In addition, since the heat energy of the coolant 151 raised in temperature through the fifth heat exchanger 152 is fully utilized, the coolant 151 is cooled again to circulate back to the cooling line 150 or discharged into the sea. can do. Since the cooling water 151 emits heat energy through the fifth heat exchanger 152, it is possible to prevent the destruction of the marine ecosystem due to the temperature rise of sea water.

When the absorption refrigerator 100 is used for the gas reliquefaction process, the cooling object 160 may be a circulating gas as well as an evaporation gas. That is, when using the circulating indirect cooling method for the overall cooling of the cargo space, an embodiment using the absorption type refrigerator 100 and using the circulating gas as the cooling object 160 may be considered.

Rearranging the refrigeration process of the absorption chiller 100 according to the present invention in sequence as follows.

(a) The cooling object 160 is cooled and liquefied by continuous evaporation of the refrigerant 131 in the evaporator 130 maintained at a low pressure. The cooled object 160 is optionally liquefied sufficiently through the second auxiliary cooler 165 and then transferred to the object tank 166. The refrigerant 131 in the evaporated gas state is transferred to the absorber 140.

(b) In the absorber 140, the absorbent 141 absorbs the refrigerant 131 to form the mixture 142. In this absorption process, the cooling water 151 may be utilized to maintain a proper temperature.

(c) The mixture 142 generated in the absorber 140 is selectively heated through the third heat exchanger 143, the second heat exchanger 163, and the fourth heat exchanger 144 in sequence. It is then transferred to the regenerator 110. The regenerator 110 utilizes the engine waste heat 170 as a heat source to heat the mixture 142 and separate and extract the refrigerant 131 and the absorbent 141.

(d) The high temperature and high pressure refrigerant 131 separated from the regenerator 110 is transferred to the condenser 120 to condense. The absorbent 141 separated from the regenerator 110 is selectively heat exchanged through the third heat exchanger 143 and then returned to the absorber 140.

(e) The refrigerant 131 condensed in the condenser 120 selectively discharges thermal energy through the first heat exchanger 161 and returns to the evaporator 130. The refrigerant 131 is circulated in the process (a) ~ (e) in this way.

(f) The cooling object 160 generated in the cooling object tank 166 selectively absorbs thermal energy through the first heat exchanger 161. The cooling object 160 converted to a state of room temperature is compressed while passing through the compressor 162, and the cooling object 160 in a high temperature and high pressure state is optionally a second heat exchanger 163 and the first auxiliary cooler. Temperature decreases via 164. The cooling object 160 is liquefied through heat exchange in the evaporator 130, and further passes through the second auxiliary cooler 165 when necessary for liquefaction according to the type of the cooling object 160. The liquefied cooling object 160 returns to the cooling object tank 166.

The technical idea should not be interpreted as being limited to the above-described embodiment of the present invention. Various modifications may be made at the level of those skilled in the art without departing from the spirit of the invention as claimed in the claims. Therefore, such improvements and modifications fall within the protection scope of the present invention as long as it is obvious to those skilled in the art.

1 is a structural diagram showing a schematic configuration of a conventional absorption chiller.

Figure 2 is a flow chart showing the schematic configuration of the gas reliquefaction process in a conventional LPG carrier.

Figure 3 is a structural diagram showing a schematic configuration of the absorption chiller using the engine waste heat according to the present invention.

<Description of the symbols for the main parts of the drawings>

10: absorption chiller 11: regenerator

12 condenser 13 evaporator

14 absorber 15 cooling tower

20: cargo hold 21: low temperature compressor

22: economizer 23: condenser

24: cooling flash valve

100: Absorption Chiller

110: regenerator 120: condenser

130: evaporator 131: refrigerant

140: absorber 141: absorbent

142 mixture 143 third heat exchanger

144: fourth heat exchanger 150: cooling line

151: coolant 152: fifth heat exchanger

155: cooling water tank 160: cooling object

161: first heat exchanger 162: compressor

163: second heat exchanger 164: first auxiliary cooler

165: second secondary cooler 166: cooling object tank

170: engine waste heat 171: first engine waste heat

172: second engine waste heat

Claims (13)

In the absorption chiller using the engine waste heat provided in the drive body using the engine as a drive source, A regenerator that uses at least one engine waste heat 170 as a heat source and heats the mixture 142 in which the absorbent 141 and the refrigerant 131 are mixed to separate and extract the refrigerant 131 and the absorbent 141. 110; A condenser (120) for condensing the refrigerant (131) in the gas phase separated from the regenerator (110) using cooling water (151); An evaporator (130) for absorbing thermal energy from the outside by evaporating the refrigerant (131) of the liquid phase condensed in the condenser (120) at low pressure; The coolant 151 absorbs the refrigerant 131 evaporated from the evaporator 130 into the absorbent 141 to generate the mixture 142, and maintains a temperature suitable for the reaction of generating the mixture 142. Absorber 140 for cooling by using to produce the mixture 142; And, The evaporator (130) is an absorption chiller using the engine waste heat, characterized in that for absorbing heat energy from the cooling object (160) passing through the periphery of the evaporator (130). The method of claim 1, The engine waste heat 170 is any one selected from the first engine waste heat 171 or the second engine waste heat 172, The first engine waste heat 171 is heat generated from any one selected from the exhaust gas of the engine or steam heated using the exhaust gas of the engine, The second engine waste heat (172) is absorption chiller using the engine waste heat, characterized in that the heat generated from the cooling water used to cool the engine. The method of claim 2, The condenser 120 and the evaporator 130 such that the refrigerant 131 moving from the condenser 120 to the evaporator 130 and the cooling object 160 passing through the periphery of the evaporator 130 exchange with each other. A first heat exchanger 161 provided on the flow path between the shells; The compressor 162 is provided on a path through which the cooling object 160 passed through the first heat exchanger 161 flows in order to compress the cooling object 160 heat exchanged in the first heat exchanger 161. ; Including, The cooling object (160) compressed by the compressor (162) is transferred to the periphery of the evaporator (130), the absorption chiller using the engine waste heat, characterized in that the cooling after delivering heat energy to the evaporator (130). The method of claim 3, wherein The absorber such that the cooling object 160 moving through the compressor 162 to the periphery of the evaporator 130 and the mixture 142 moving from the absorber 140 to the regenerator 110 exchange with each other. Absorption freezer using the engine waste heat, characterized in that it comprises a second heat exchanger (163) provided on the flow path between the 140 and the regenerator (110). The method of claim 4, wherein The absorber 140 and the absorber 141 moving from the regenerator 110 to the absorber 140 and the mixture 142 moving from the absorber 140 to the regenerator 110 are mutually heat exchanged. It includes a third heat exchanger 143 provided on the flow path between the regenerator 110, The mixture 142 moving from the absorber 140 to the regenerator 110 passes through the third heat exchanger 143 and then flows into the second heat exchanger 163. Absorption chiller used. The method of claim 5, On the flow path between the absorber 140 and the regenerator 110 to heat the mixture 142 moving from the absorber 140 to the regenerator 110 using the second engine waste heat 172 as a heat source. Including a fourth heat exchanger 144 provided in, The mixture 142 moving from the absorber 140 to the regenerator 110 passes through the second heat exchanger 163 and then flows into the fourth heat exchanger 144. Absorption chiller used. The method of claim 6, A first auxiliary cooler 164 is provided on the flow path between the second heat exchanger 163 and the evaporator 130 to assist cooling of the cooling object 160 that has passed through the second heat exchanger 163. Absorption chiller using the engine waste heat, characterized in that provided. The method of claim 7, wherein the absorbent 141 and the refrigerant 131 Absorber using engine waste heat, characterized in that using the water (H2O) as the absorbent (141) and ammonia (NH3) as the refrigerant (131). The method of claim 7, wherein the absorbent 141 and the refrigerant 131 Lithium bromide (LiBr) as the absorbent (141) and water (H 2 O) as the refrigerant 131, the absorption chiller using the engine waste heat, characterized in that. The method according to any one of claims 1 to 9, The cooling object 160 is an absorption chiller using an engine waste heat, characterized in that the evaporated gas evaporated from any one selected from liquefied petroleum gas (LPG), liquefied natural gas (LNG), carbon dioxide (CO2). 11. The method of claim 10, The cooling water 151 is an absorption chiller using the engine waste heat, characterized in that the sea water. The method of claim 11, The cooling line 150 through which the cooling water 151 flows is provided with a fifth heat exchanger 152 for using thermal energy of the cooling water 151 used for cooling in the absorber 140 and the condenser 120. Absorption chiller using the waste heat of the engine, characterized in that. 13. The method of claim 12, When the cooling object 160 is liquefied natural gas (LNG), In order to assist cooling of the cooling object 160 passing through the periphery of the evaporator 130, a second auxiliary cooler 165 is provided in the flow path of the cooling object 160 passing through the periphery of the evaporator 130. Absorption freezer using the engine waste heat, characterized in that provided.

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