KR20110032860A - An environment friendly refrigeration system using waste heat of a large-capacity compressor - Google Patents

Abstract

PURPOSE: A cooling device using the waste heat of a compressor is provided to increase the effective driving pressure ratio of an ejector since the water is heated at a constant temperature and the pressure of a cooling cycle is decreased. CONSTITUTION: A cooling device using the waste heat of a compressor comprises a storage tank(20), a compressor(40), and a power cycle unit(100). The storage tank stores a first heat exchange medium. The first heat exchange medium has fluidity and a heat transfer property. The compressor heats fluid medium at a high temperature and then discharges it. The power cycle unit collects the heat through the first heat exchange medium, which heat-exchanges with the heated fluid medium.

Description

Cooling system using waste heat of compressor {AN ENVIRONMENT FRIENDLY REFRIGERATION SYSTEM USING WASTE HEAT OF A LARGE-CAPACITY COMPRESSOR}

The present invention relates to a cooling apparatus using waste heat of a compressor, and more particularly, to an environment-friendly facility for heating water, which is a natural refrigerant, by effectively recovering a high temperature state generated at the discharge port of each stage of the compressor, and always maintaining a constant temperature through the compressor waste heat. Water can be heated to reduce the environmental impact and improve the heatability of the water.It is not subject to any weather conditions or time constraints to increase its utilization, and to increase the temperature recovery rate by using the high temperature waste heat of the compressor. It relates to a cooling device using the waste heat of the compressor.

Many methods have been devised to achieve a conventional cooling or freezing effect.

These methods include the most basic conventional methods using frost or artificial ice, mechanical compression using various refrigerants, absorption using refrigerants and absorbents, vacuum methods to lower the pressure to obtain cooling effects, and to pass current through semiconductors. It can be classified into an electronic refrigeration method using the generated Peltier effect.

When using a volatile liquid, that is, a refrigerant, heat exchange with the surrounding medium is performed through a series of iterative processes of compressing, condensing, and evaporating the refrigerant. This mechanical compression method requires a considerable amount of power to operate the compressor and has the disadvantage of using various refrigerants, which are the main causes of global warming, but the coefficient of performance (COP) of the refrigeration cycle is higher than that of other methods. It has been used a lot in the past.

In addition, the absorption type uses a material capable of absorbing a large amount of vapor generated when the refrigerant evaporates, that is, an absorption material, and uses a chemical absorption process generated in the absorbent. Recently, due to the problem of global warming, the use of CFC or HCFC system refrigerants is extremely limited, and there are a lot of absorption air-conditioning and heating devices that apply solar heat to LiBr (Lithium Bromide), water, and refrigeration units using ammonia and water as environmentally friendly refrigerants. It is proposed.

In conventional absorption cooling systems, water is evaporated in the evaporator under vacuum pressure and absorbed by the aqueous LiBr solution in the absorber. The dilute solution which absorbs water is heated and evaporated by the solar heat source obtained from the solar collector through the heat exchange tank, and made into a thick solution and sent to the absorber.

The steam generated in the heat exchange tank is condensed into water in the condenser and sent to the evaporator. In this process, heat is removed from the ambient as much as the latent heat of evaporation of the refrigerant to obtain a cooling state.

In order to smoothly operate the absorption cooling system, a plurality of circulation pumps are required, and a cooling tower for supplying cooling water is required.

In addition, although the solar heat is somewhat different depending on the temperature fluctuations and the characteristics of the collector, the energy level is much lower than the temperature obtained by using a boiler or the like. Therefore, it is true that the method of driving the ejector with conventional solar heat has not been actively studied.

Conventional cooling device using solar heat has a problem that its utilization is reduced due to a lot of time influences such as weather change, day and night or summer and winter because it uses solar heat.

In addition, since the conventional cooling device using solar heat has to use a heat collecting plate, there is a problem in that a lot of facility space is required.

In addition, the conventional cooling device using solar heat can recover the temperature only up to about 70 degrees with the current technology, there is a problem that the temperature recovery rate is lowered. Therefore, there is a need for improvement.

The present invention has been made to improve the above problems, it is possible to heat the water at a constant temperature at all times through the compressor waste heat to improve the heating properties of the water is less affected by the environment, it is not subject to any weather or time constraints The purpose of the present invention is to provide a cooling device using the waste heat of the compressor to increase the utilization as well as increase the temperature recovery rate by using the high temperature waste heat of the compressor.

A cooling apparatus using waste heat of a compressor according to the present invention includes: a storage tank for storing a first heat exchange medium having fluidity and heat transfer property, a compressor for forming a flow pipe and heating and discharging the flow medium flowing to a high temperature, and And a power cycle unit for recovering heat through the first heat exchange medium that exchanges heat with the fluid medium.

The power cycle part may include a discharge flow path tube extending from the storage tank to the flow pipe and extending from the discharge flow path tube to be in contact with the circumferential surface of the flow pipe to transfer heat from the flow medium to the first heat exchange medium. And a guide coil heating tube, and an inflow passage tube extending from the coil heating tube to the storage tank to guide the first heat exchange medium to the storage tank.

The coil heating tube is preferably protected by a heat insulating member.

The storage tank is formed at a position higher than the flow pipe, the discharge flow path pipe is provided with a circulation pump, the inflow flow path pipe is preferably formed a flow control valve.

The storage tank is preferably provided with an auxiliary heater for auxiliary heating of the stored first heat exchange medium.

Preferably, the heat exchange tank is provided with a cooling cycle part that circulates the second heat exchange medium and generates cold air.

The flow pipe is preferably formed to project the vortex generating protrusions on the inner side.

In addition, the vortex generating protrusion is preferably provided with a sphere-shaped fluid therebetween.

In particular, it is preferable that the vortex generating protrusions form a vertical surface perpendicular to the flow pipe at portions facing each other.

As described above, the cooling device using the waste heat of the compressor according to the present invention can heat the water at a constant temperature at all times through the waste heat of the compressor, unlike the prior art, thereby improving the heatability of the water due to less environmental influence, Not only is it time-limited, the utilization is not only increased, but the high temperature waste heat of the compressor can be used to increase the temperature recovery rate.

The present invention can increase the effective operating pressure ratio of the ejector by lowering the pressure of the cooling cycle to increase the pressure of the compressor heating cycle, and to increase the evaporation effect of the water.

In addition, the present invention can increase the thermosiphon circulation effect of the fluid in the cooling cycle by installing the positions of the storage tank and the condenser above the power cycle unit.

In addition, the present invention can increase the power generation efficiency by installing a heat exchange tank inside the storage tank to efficiently perform heat exchange of water through the waste heat of the compressor.

In addition, the present invention does not require various conventional circulation pumps, cooling towers, and the like, and can realize a simple structure.

Hereinafter, with reference to the accompanying drawings will be described an embodiment of a cooling device using the waste heat of the compressor according to the present invention. In this process, the thickness of the lines or the size of the components shown in the drawings may be exaggerated for clarity and convenience of description. In addition, the terms described below are defined in consideration of the functions of the present invention, which may vary depending on the intention or custom of the user, the operator. Therefore, definitions of these terms should be made based on the contents throughout this specification.

1 is a diagram schematically illustrating a cycle of a cooling apparatus using waste heat of a compressor according to an embodiment of the present invention, and FIG. 2 is a schematic diagram of a multi-stage cycle of a cooling apparatus using waste heat of a compressor according to an embodiment of the present invention. This is the main part diagram.

3 to 5 are cross-sectional views of the tube showing the vortex generation state in the cooling device using the waste heat of the compressor according to various embodiments of the present invention.

6 is a discharge temperature-compression ratio diagram in a cooling apparatus using waste heat of a compressor according to an embodiment of the present invention.

1, the cooling device using the waste heat of the compressor according to an embodiment of the present invention, the heat exchange tank 10, the storage tank 20, the flow pipe 30, the compressor 40 and the power cycle unit 100 ).

The heat exchange tank 10 stores a first heat exchange medium having fluidity and heat transfer property therein. In this case, the first heat exchange medium may be applied to various media, but is preferably water.

In addition, the storage tank 20 is provided inside the heat exchange tank 10.

At this time, the storage tank 20 stores a second heat exchange medium having fluidity and heat transfer property. The second heat exchange medium can be any of a variety of media, but is preferably water.

In particular, although not shown, the storage tank 20 is sufficiently sealed in the heat exchange tank 10 so that the first heat exchange medium and the second heat exchange medium are not mixed.

Therefore, since the storage tank 20 is immersed in the first heat exchange medium of the heat exchange tank 10, heat loss may be minimized due to contact with the outside during heat exchange while directly exchanging heat with the first heat exchange medium.

In particular, the storage tank 20 is applicable to a variety of shapes and materials.

In addition, the flow pipe 30 serves to guide the flow of the flow medium. In particular, the fluidized medium may be applied to various media, but is preferably air.

Therefore, the flow pipe 30 is a pipe for guiding the flow medium.

The flow pipe 30 is applicable to various shapes and various materials. In addition, the flow pipe 30 may form a closed curve to guide the circulating flow of the fluid, but it is preferable to supply the fluid to one side and to discharge the fluid to the other side.

In addition, the compressor 40 is formed in the flow pipe 30 and serves to discharge and discharge the flow medium flowing from one side of the flow pipe 30 to the other direction at a high temperature.

Therefore, the fluid medium is brought into a high temperature and high pressure state by passing through the compressor 40.

The compressor 40 is connected to the flow pipe 30 may be variously applied, such as bolting.

In particular, in the case of a large-capacity air compressor, the process of compressing the air in the atmosphere is close to the adiabatic compression process.

Thus, as given by the following equation, the temperature of the air increases in the process of compressing the air.

In other words,

Here, P1 and T1 are the pressure and temperature of the air before compression, P2 and T2 are the pressure and temperature of the air after compression, respectively, and k is the ratio of specific heats of the air.

On the other hand, the power cycle unit 100 serves to heat exchange the high temperature heat obtained through this principle with the fluid.

That is, the power cycle unit 100 circulates the first heat exchange medium into the heat exchange tank 10 and supplies maximum heat energy to the first heat exchange medium stored in the heat exchange tank 10 using the waste heat of the compressor 40. It plays a role.

In more detail, the power cycle unit 100 includes a discharge flow path tube 110, a coil heating tube 120 and an inlet flow path tube 130.

The discharge flow path tube 110 extends into the flow pipe 30 in the heat exchange tank 10, and the coil heating tube 120 extends from the discharge flow path tube 110 to be directly connected to the circumferential surface of the flow pipe 30. Is formed to be in contact with, the inflow passage tube 130 extends from the coil heating tube 120 serves to be inserted into the storage tank 20.

Accordingly, the first heat exchange medium stored in the heat exchange tank 10 is circulated along the discharge flow path tube 110, the coil heating pipe 120, and the inflow flow path tube 130.

At this time, the flow medium in the high temperature and high pressure state flows inside the flow pipe (30).

In addition, the flow pipe 30 and the coil heating tube 120 is preferably made of a material having excellent heat transfer. Of course, the discharge flow path tube 110, the coil heating tube 120 and the inlet flow path tube 130 is preferably molded integrally.

Thus, since the coil heating tube 120 is in contact with the flow pipe 30, the first heat exchange medium is introduced into the heat exchange tank 10 in a heated state as it heat exchanges with the flow medium.

Here, the coil heating tube 120 may be in contact with the circumferential surface of the flow pipe 30 in various ways, it is preferred to maximize the contact area by winding in a coil method.

In addition, the discharge flow path tube 110, the coil heating tube 120 and the inlet flow path tube 130 is not limited to be provided with various diameters and various numbers.

In addition, a part of the discharge channel 110, the coil heating tube 120 and a part of the inlet channel 130 may be axially inserted into the flow pipe (30).

On the other hand, the portion where the flow pipe 30 and the coil heating tube 120 is in contact is preferably sealed from the outside to reduce the heat exchange loss.

Therefore, the coil heating tube 120 wound around the circumferential surface of the flow pipe 30 is preferably installed to be wrapped in the heat insulating member 140.

Of course, the heat insulating member 140 is preferable to minimize the heat loss wrapped around the discharge flow path tube 110, the coil heating pipe 120 and the inlet flow path tube 130.

At this time, the flow pipe 30 may be provided to be wrapped by the heat insulating member 140 only a part in contact with the coil heating tube 120, it may be wrapped around the whole heat insulating member 140.

For convenience, the heat insulating member 140 is shown diagrammatically applicable to a variety of thermal pads.

In addition, the first heat exchange medium of the heat exchange tank 10 may naturally flow through the discharge flow path tube 110 to the coil heating tube 120.

Thus, the heat exchange tank 10 is provided at a position higher than the flow pipe 30. This is to enable the first heat exchange medium to effectively convert the potential energy due to the drop Δh into kinetic energy so as to effectively generate the circulation of the first heat exchange medium.

In addition, the condenser 230, which will be described later, is provided at a position higher than the flow pipe 30.

And, since the heat exchange tank 10 is provided at a position higher than the flow pipe 30, the first heat exchange medium can be naturally circulated, but there may be a limitation in the flow rate of the flow rate.

Therefore, it is preferable that the circulation pump 150 is provided on the discharge flow path tube 110.

This is to maintain a constant circulation flow rate and circulation flow rate by forcibly circulating the first heat exchange medium stored in the heat exchange tank 10 by the operation of the circulation pump 150.

On the other hand, the heat exchange tank 10 is filled with a first heat exchange medium therein.

In particular, the manner in which the circulation pump 150 is provided in the discharge channel 110 is a general one. Of course, the circulation pump 150 may be formed in the inlet flow pipe 130, or may be applied to various models.

In addition, the inflow passage 130 is provided with a flow control valve 160.

The flow rate control valve 160, which will be described later, circulates inside the discharge flow path tube 110, the coil heating tube 120 and the inlet flow path tube 130 according to the size of the cooling load generated in the cooling cycle unit 200. It serves to adjust the flow rate of the first heat exchange medium.

In particular, the flow rate control valve 160 and the circulation pump 150, although not shown, it is preferably electrically connected to the flow meter formed in the main pipe member 210 is controlled mutually.

Of course, the flow control valve 160 may be formed in the discharge flow path pipe 110, it is applicable to various models.

In addition, since the first heat exchange medium stored in the heat exchange tank 10 and circulated and heated may not rise to an operation error or a set temperature of the compressor 40, the heat exchange tank 10 includes the auxiliary heater 170.

The auxiliary heater 170 serves to auxiliary heating the first heat exchange medium stored in the heat exchange tank (10). This is to continuously supply sufficient thermal energy to the storage tank 20 provided in the heat exchange tank 10.

Here, the auxiliary heater 17 is fixed to the inner wall of the heat exchange tank 10 can be applied to various attachments.

In particular, the storage tank 20 is installed inside the heat exchange tank 10 to receive sufficient heat transfer from the first heat exchange medium heated by the compressor 40.

At this time, the storage tank 20 stores the second heat exchange medium therein.

Here, the first heat exchange medium circulates inside and outside the heat exchange tank 10, and the second heat exchange medium circulates inside and outside the storage tank 20.

At this time, the heat exchange tank 10 and the storage tank 20 may be made of a material such as steel having excellent heat transfer properties and may be located as close as possible or may be installed to be in close contact with each other so that heat exchange between the fluid medium and the first heat exchange medium is sufficiently performed. However, it is preferable that the storage tank 20 is mounted inside the heat exchange tank 10.

In addition, Figure 2 is another embodiment of the present invention the power cycle unit 100 of the cooling device using the waste heat of the compressor is realized in multiple stages. For convenience, the power cycle unit 100 is shown to consist of three stages.

That is, the flow pipes 30a, 30b, 30c are independently connected to each of the three compressors 40a, 40b, and 40c.

In particular, when the compression ratio becomes 9 to 10 or more from the viewpoint of the efficiency of the compressors 40a to 40c and the ease of design / manufacturing, the compression process is designed in multiple stages.

At this time, since the temperature of the compressed air in the first stage is increased, the hot air should be compressed at the second stage inlet.

In other words,

Will be satisfied.

Where Lad is the power (kW) required to compress the pressure P1 to P2 in an isentropic process, P1 is the absolute pressure of the intake air of the compressor (MPa), and P2 is the absolute pressure of the discharged air (MPa) and Q1 is the suction Flow rate (m 3 / min).

Thus, the amount of work required to compress the air becomes larger as the temperature of the air increases and as the compression ratio increases.

In particular, in the case of a compressor with a high compression ratio, it is compressed in multiple stages to reduce the compression (Lad). In this case, the air compressed in the first stage is extracted and cooled (called Inter Cooler), and then subjected to two stage compression again, and then cooled again to undergo a three stage compression process.

In addition, in one storage tank 20, the discharge flow path tube 110a, the coil heating tube 120a, and the inflow channel tube 130a form a closed curve, and the discharge flow path tube 110b, the coil heating tube 120b, and the like. The inflow channel 130b forms a closed curve, and the discharge channel 110c, the coil heating tube 120c and the inflow channel 130c form a closed curve.

Of course, the heat insulating members 140a, 140b and 140c, the circulation pumps 150a, 150b and 150c and the flow control valves 160a, 160b and 160c are formed to correspond to the above-described positions, respectively.

In addition, the function of each component replaces the above-mentioned thing. In addition, the reference numerals are replaced with those described above.

On the other hand, the heat of the heat exchange tank 10 obtained through the power cycle unit 100 is heat-exchanged with the second heat exchange medium in the storage tank 20.

In particular, the cooling cycle unit 200 includes a main pipe member 210, an ejector 220, a condenser 230, a branch pipe member 240, an expansion valve 250 and an evaporator 260.

At this time, the power cycle unit 100 and the cooling cycle unit 200 uses water as a medium, the power cycle unit 100 is set to maintain a pressure slightly higher than the atmospheric pressure or atmospheric pressure, the cooling cycle unit 200 Is set to a pressure lower than atmospheric pressure in order to easily achieve the saturated steam pressure of water at the set storage tank 20 temperature.

As such, the pressure ratio generated by the two cycle parts 100 and 200 may be the driving pressure ratio of the ejector 220, and may effectively drive the ejector 220.

In particular, the operation of the cooling cycle unit 200 is lower than atmospheric pressure as the second heat exchange medium by heating the second heat exchange medium stored in the storage tank 20 in the heat exchange tank 10 with the heat obtained from the waste heat of the compressor 40. Produces saturated steam at vacuum pressure.

The saturated steam is used as a driving fluid of the ejector 220, that is, the second heat exchange medium, and is discharged at supersonic speed through the enlarged expansion nozzle 222 of the ejector 220.

In this case, the low pressure steam generated in the evaporator 260 is sucked by the shear action and the pressure drop action generated in the supersonic airflow.

Due to this action, the temperature of the water inside the evaporator 260 is reduced.

On the other hand, the two fluids sucked with the driving fluid in the mixing unit 226 of the ejector 220 is mixed and decelerated in the diffuser 228 to recover the pressure to the pressure generated at the inlet of the condenser 230.

The compressed steam as described above is cooled with water in the condenser 230 to partially complete the cycle while being partially introduced into the evaporator 260 through the expansion valve 250 and the remaining into the storage tank 20.

At this time, in order to increase the pressure of the water generated in the condenser 230 to the pressure of the storage tank 20, it is preferable to install the storage tank 20 far below the condenser 230.

Then, the water can be effectively circulated inside two cycles of heating and cooling without using a conventional circulation pump.

 In particular, the second heat exchange medium heated in the storage tank 20 and converted into a gaseous phase in a high temperature and high pressure state circulates to the cooling cycle part 300, generates cold air, and then flows into the storage tank 20.

More specifically, the main tube member 210 is formed to draw a closed curve in the storage tank 20 to circulate the second heat exchange medium. That is, the main pipe member 210 serves to circulate the second heat exchange medium discharged from the storage tank 20 and to supply it to the storage tank 20 again.

At this time, the main tube member 210 is connected to the storage tank 20 is sealed, the second heat exchange medium flows in or around the storage tank 20, the heat exchange tank 10 containing the storage tank 20 Heat energy is supplied.

The storage tank 20, the ejector 220, and the condenser 230 are connected to the main pipe member 210 forming a closed curve to enable circulation of the second heat exchange medium.

In addition, the expansion valve 250 and the evaporator 260 is connected to the branch pipe member 240 across the main pipe member 210 forming a closed curve.

At this time, although not shown, the main pipe member 210 is connected to the storage tank 20, the ejector 220, and the condenser 230 by various methods capable of sufficiently sealing.

In addition, although not shown, the branch pipe member 240 is connected to the expansion valve 250 and the evaporator 260 by various ways capable of sufficiently sealing.

In addition, although not shown, the main pipe member 210 and the branch pipe member 240 may be connected to be separated from each other to be sealed, or may be integrally connected by welding or the like.

In detail, the main pipe member 210 forms a closed curve for circulating the second heat exchange medium in the storage tank 20 to circulate the second heat exchange medium in a gaseous state at high temperature and high pressure.

The second heat exchange medium naturally flows to the ejector 220 along the main tube member 210.

That is, the second heat exchange medium, which is a gaseous state of high temperature and high pressure in the storage tank 20, flows into the ejector 220 while naturally rising through the main pipe member 210 as the specific gravity is low as it is in a gaseous state.

At this time, the storage tank 20 is filled with the second heat exchange medium.

In addition, the ejector 220 is formed in the main pipe member 210 to convert the pressure energy of the second heat exchange medium, which is a gaseous phase of high temperature and high pressure, discharged from the storage tank 20 into velocity energy, thereby expanding under reduced pressure. do.

At this time, the ejector 220 passes through the evaporator 260 and introduces a second heat exchange medium which is a low-temperature, low-pressure gas phase.

That is, the ejector 220 is a reduction enlargement nozzle 222 for introducing a second heat exchange medium that is a high temperature and high pressure gas discharged from the storage tank 20, and the supersonic velocity of the second heat exchange medium passing through the reduction expansion nozzle 222. Inlet 224 for sucking the second heat exchange medium, which is a low temperature low pressure gaseous phase, generated in the evaporator 260 by the shear action and the pressure drop action generated by the airflow, the second heat exchange medium with high temperature and high pressure, and the second heat exchange with low temperature and low pressure. A mixing unit 226 for mixing the medium to lower the temperature and a diffuser 228 for compensating for the reduced pressure by decelerating the mixed and cooled second heat exchange medium.

In particular, the ejector 220 may be made of various shapes and various materials.

In addition, the condenser 230 is formed in the main pipe member 210 and passes through the ejector 220 to discharge the second heat exchange medium heat expanded under reduced pressure in the air at room temperature to condense liquefaction.

Therefore, the second heat exchange medium passing through the condenser 230 is circulated as it flows into the storage tank 20.

On the other hand, the branch pipe member 240 is branched from the main pipe member 210 extending from the condenser 230 is connected to the ejector 220. The branch pipe member 240 is connected to the main pipe member 210 by welding or the like.

In addition, the expansion valve 250 is formed on the branch pipe member 240 to condense and liquefy the second heat exchange medium, which is partially branched and flows after the condensation liquefaction in the main pipe member 210, serves to insulate and liquefy by low temperature and low pressure. do.

In addition, the evaporator 260 is formed in the branch member 240 to absorb the latent heat of evaporation from the second heat exchange medium that is adiabatic expansion from the expansion valve 250 serves to cool.

In addition, the second heat exchange medium, which is a low-temperature, low-pressure gaseous phase that absorbs heat and evaporates, is transferred to the ejector 220 by an external force.

In particular, it is preferable that the fluidized medium passing through the compressor 40 can further generate heat energy.

This is to increase the temperature of the cold air discharged by increasing the temperature of the second heat exchange medium flowing into the storage tank 20 and to improve the cooling power.

As a first embodiment, referring to FIG. 3, the flow pipe 30 protrudes and forms the vortex generating protrusion 310a on the inner surface.

Heat flow is promoted when the flow of the circulating fluid circulating inside the flow pipe 30 becomes turbulent flow, compared to the case of laminar flow, so that the vortex generating protrusion 310a heats the flow medium through resistance. To supply energy.

In particular, the vortex generating protrusion 310a is preferably formed in a triangular blade form to effectively increase the vortex component.

Of course, the vortex generating protrusion 310a can be modified into various shapes and various materials. In addition, the vortex generating protrusion 310a is not limited to the number, and although not illustrated, the vortex generating protrusion 310a may be detachably formed on the flow pipe 30 by a bolting method.

Meanwhile, as a second embodiment, referring to FIG. 4, the vortex generating protrusion 310b is formed to protrude toward the center of the flow pipe 30. That is, the vortex generating protrusion 310b is naturally formed at the time of forming the flow pipe 30.

At this time, the vortex generating protrusion 310b can be modified in various shapes and various numbers.

In addition, as a third embodiment, referring to FIG. 5, the vortex generating protrusion 310c protrudes from the inner surface of the flow pipe 30 to form a vortex generating protrusion 310c spaced at regular intervals with respect to the flow direction of the flow medium. do.

A spherical fluid 320 is provided between the vortex generating protrusions 310c spaced apart from each other.

The fluid 320 vibrates irregularly in an upstream or downstream direction of the flow or in a direction perpendicular to the induction due to a vortex (Karman Vortex) generated relatively downstream by the flow of the fluid medium.

The vibration of the fluid 320 is to further promote the vortex inside the flow pipe 30 can improve the heat exchange performance.

Here, the fluid 320 may be applied in various shapes, and may be formed of a material similar to or specific to the specific gravity of the flowing fluid medium.

In particular, the flow pipe 30 is preferably formed detachably so as to install or exchange the flower 320 therein.

In addition, the vortex generating protrusion 310c forms a vertical surface 330 perpendicular to the axial direction of the flow pipe 30 at portions facing each other with respect to the flow direction of the flow medium.

This is to prevent the departure of the fluid 320 and to increase the thermal energy supplied to the fluid by generating sufficient vortex in the vertical plane 330.

6 shows the temperature of air generated at the discharge port of a typical large centrifugal turbo compressor installed in a large number of plants as a function of the compression ratio. From the figure, as the compression ratio increases, the air temperature at the discharge port of the compressor increases. In the case of a multi-stage compressor, the temperature of the compressed air at the discharge port is somewhat lower than that of the first stage even though the compressed heated air is cooled in the first stage outlet, compressed in the second stage, and then cooled again and compressed in the third stage, but still very much. It becomes a high temperature. Due to this high temperature, not only a large after cooler is required at the discharge port of the compressor but also a temperature increase inside the factory, which adversely affects the operating environment.

Thus, in the case of a compressor having a high compression ratio, it is compressed in multiple stages to reduce the compression (Lad). In this case, the compressed air is extracted from the first stage and cooled (called Inter Cooler), and then subjected to two stage compression again, and then cooled again to undergo a three stage compression process.

Although the present invention has been described with reference to the embodiments shown in the drawings, this is merely exemplary, and those skilled in the art to which the art belongs can make various modifications and other equivalent embodiments therefrom. I will understand. Therefore, the true technical protection scope of the present invention will be defined by the claims below.

1 is a diagram schematically showing a cycle of a cooling apparatus using waste heat of a compressor according to an embodiment of the present invention.

2 is a main diagram schematically showing a multi-stage cycle of a cooling apparatus using waste heat of a compressor according to an embodiment of the present invention.

3 to 5 are cross-sectional views of the tube showing the vortex generation state in the cooling device using the waste heat of the compressor according to various embodiments of the present invention.

6 is a discharge temperature-compression ratio diagram in a cooling apparatus using waste heat of a compressor according to an embodiment of the present invention.

<Explanation of symbols on main parts of the drawings>

10: heat exchange tank 20: storage tank

30: flow pipe 40: compressor

100: power cycle unit 110: discharge flow path tube

120: coil heating tube 130: inlet flow tube

140: heat insulating member 150: circulation pump

160: flow control valve 170: auxiliary heater

200: cooling cycle section 210: main pipe member

220: ejector 230: condenser

240: branch pipe member 250: expansion valve

260: evaporator 310a, 310b, 310c: vortex generation protrusion

Claims (10)

A storage tank storing the first heat exchange medium having fluidity and heat transfer property; A compressor which is formed in the flow pipe and heats and discharges the flowing fluid medium at a high temperature; And And a power cycle unit for recovering heat through the first heat exchange medium that exchanges heat with the heated fluid medium. The method of claim 1, wherein the power cycle unit, A discharge flow channel extending from the storage tank to the flow pipe; A coil heating tube extending from the discharge flow path tube and formed in contact with a circumferential surface of the flow pipe to transfer heat of the flow medium to the first heat exchange medium; And And an inlet flow channel extending from the coil heating tube to the storage tank to guide the first heat exchange medium to the storage tank. 3. The method of claim 2, Cooling device using the waste heat of the compressor, characterized in that the coil heating tube is protected by a heat insulating member. The method of claim 2 or 3, The storage tank is a cooling device using waste heat, characterized in that formed in a position higher than the flow pipe. The method of claim 2 or 3, The discharge flow path tube includes a circulation pump; The inlet flow pipe is a cooling device using the waste heat of the compressor, characterized in that to form a flow control valve. The method according to any one of claims 1 to 3, The storage tank is a cooling device using the waste heat of the compressor, characterized in that it comprises an auxiliary heater for auxiliary heating the stored first heat exchange medium. The method of claim 6, The storage tank has a heat exchange tank having a fluidity and heat transfer property and storing a second heat exchange medium heated by heat exchange with the first heat exchange medium; The heat exchange tank is a cooling device using the waste heat of the compressor, characterized in that for supplying a natural circulation of the second heat exchange medium heated in the cooling cycle unit. The method of claim 6, The flow pipe is a cooling device using the waste heat of the compressor, characterized in that the protrusion to form a vortex generating protrusion on the inner side. The method of claim 8, Cooling device using the waste heat of the compressor, characterized in that the vortex generating protrusion is provided with a sphere-shaped fluid therebetween. The method of claim 8, And the vortex generating protrusions form a vertical plane perpendicular to the flow pipe at portions facing each other.

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