KR101680516B1 - Load adaptive type micro-combined heat and power supply system - Google Patents

Abstract

The present invention relates to a load adaptive type micro-combined heat and power supply system, which can supply heating or hot water in addition to power generation with a micro-combined heat and power generator, and further, can be continuously operated even if there is no an electricity load or a heating / cooling load.

Description

[0001] The present invention relates to a load adaptive cogeneration system,

The present invention relates to a load adaptive cogeneration system capable of supplying heating or hot water with power generation using a micro-cogeneration apparatus, and also capable of continuous operation even when there is no power load or no heating / cooling load.

Recently, a micro-Combined Heat and Power System (m-CHP) that can be applied to both domestic and industrial applications due to its high energy efficiency has been proposed while solving the shortcomings of district heating and individual heating.

The miniature cogeneration system is a total energy system that simultaneously generates power and heat from a single energy source. Generally, the high temperature unit is used as a power source for generating electric power and the low temperature unit is used as a heat source.

For example, Korean Unexamined Patent Publication No. 2006-0013391 or Korean Patent No. 1264249 uses an engine to drive a generator, and waste heat generated in the process is recovered through a heat exchanger to supply hot water or heating water.

However, in the conventional technology as described above, normal operation can be performed only when there is power or heating load when the cogeneration system is in operation, and there is a problem that normal operation is difficult when there is no load.

For example, when there is no power load, the power must be discarded or the power generation must be stopped. If there is no heating load, the heat can not be discharged, resulting in overheating of the system.

Patent Document 1. Korean Patent Publication No. 2006-13391 Patent Document 2. Korean Patent No. 1264249

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems, and it is an object of the present invention to provide a compact cogeneration power generation apparatus capable of supplying heating or hot water together with power generation and also capable of continuously operating even when there is no power load or heating / And to provide a load-adaptable cogeneration system as possible.

To this end, the load adaptive cogeneration system according to the present invention comprises an engine; A generator driven by the engine to produce electricity; A heating device for supplying heating or hot water to the load side; A storage tank for storing hot water and supplying the hot water to the heating device; A cooling water circulation pipe circulating the cooling water to collect waste heat in a process of cooling while passing through the generator and the engine; A waste heat recovery heat exchanger in which the cooling water supplied from the cooling water circulation pipe passes through the primary side and the water in the storage tank passes through the secondary side to perform water to water heat exchange; And a heater for heating the water in the thermal storage tank, wherein the heater is electrically connected to receive power of the generator, and when the power load is not present or is insufficient, the heater is operated by electricity generated from the generator, Is heated.

A direct water pipe for supplying low-temperature direct water to the secondary side of the waste heat recovery heat exchanger; And a water discharge pipe for discharging the hot water stored in the thermal storage tank to the outside of the system. When there is no heating load due to the heating device, low-temperature direct water is supplied through the water discharge pipe, So that the engine or the generator is not overheated so that continuous power generation is achieved.

A cooling device for supplying cooling to the load side; A cooling heat exchanger in which heat exchange is performed between a high temperature exhaust gas discharged from the engine and a heat medium for driving the air conditioner; An exhaust pipe for guiding high-temperature exhaust gas discharged from the engine to the outside after passing through the cooling heat exchanger; A heat medium circulation pipe for circulating the heat medium that has undergone the heat exchange in the cooling heat exchanger to either the cooling device or the heat storage tank; And a discharge pipe for supplying hot water stored in the thermal storage tank to one of the heating device and the cooling device, wherein when the heating load by the heating device and the cooling load by the cooling device are absent, And discharges the high temperature water stored in the heat storage tank.

Preferably, the discharge pipe is a branch discharge pipe, the first discharge end is connected to the heating device, and the second discharge end is connected to the cooling device, and the hot water stored in the storage tank is supplied to the heating device or the cooling device.

The waste heat recovery heat exchanger includes a first waste heat recovery heat exchanger and a second waste heat recovery heat exchanger that are provided independently of each other, wherein the heater includes a first heat recovery heat exchanger and a second heat recovery heat exchanger, It is preferable to heat water in the middle-temperature storage tank by being installed on the secondary side of the waste heat recovery heat exchanger.

The cooling device is a dual efficiency absorption type refrigerator driven by two heating media including steam and middle temperature water. The heating medium is steam, the cooling heat exchanger is a steam heat exchanger, and the cooling heat exchanger is a steam heat exchanger. Wherein the cooling water supplied from the cooling water circulation pipe passes through the first side of the second waste heat recovery heat exchanger and the second side of the second waste heat recovery heat exchanger is connected to the second side of the cooling water circulation pipe, And a water-to-water heat exchange is performed between the secondary heat exchanger and the cooling device so that water supplied to the intermediate-temperature water receiving portion of the cooling device passes through the secondary heat exchanger, A first heat medium circulation pipe for circulating the heat medium; A second heat medium circulation tube circulating between the cooling heat exchanger and the steam storage tank; And a three-way valve disposed in a branch passage connecting the first heat medium circulation pipe and the second heat medium circulation pipe, wherein the steam is supplied to the steam containing portion of the cooling device through the first heat medium circulation pipe, Or the steam is supplied to the second heat storage tank through the second heat medium circulation pipe to heat the water in the second heat storage tank.

The present invention as described above enables the heating or hot water to be supplied together with the power generation by using the micro-cogeneration unit at normal times.

Further, in the present invention, when there is no power load or underload, the hot water is supplied to the heater by consuming power from the heater inside the system.

In addition, the present invention enables continuous operation without overheating of the system by releasing hot water that has been stored while replenishing low-temperature direct water when there is no heating / cooling load.

1 is a diagram showing a first operation mode (heating load) of a load adaptive cogeneration system according to an embodiment of the present invention.
2 is a diagram showing a second operation mode (power load) of the load adaptive cogeneration system according to an embodiment of the present invention.
3 is a view showing a third operation mode (cooling load) of the load adaptive cogeneration system according to an embodiment of the present invention.
4 is a diagram showing a fourth operation mode (heating + power load) of the load adaptive cogeneration system according to an embodiment of the present invention.
5 is a view showing a fifth operation mode (cooling + power load) of the load adaptive cogeneration system according to an embodiment of the present invention.
6 is a diagram showing a fourth operation mode (heating + power load) of the load adaptive cogeneration system according to another embodiment of the present invention.
7 is a view showing a fifth operation mode (cooling + power load) of the load adaptive cogeneration system according to another embodiment of the present invention.

Hereinafter, a load adaptive cogeneration system according to a preferred embodiment of the present invention will be described in detail with reference to the accompanying drawings.

1 to 5, a load adaptive cogeneration system 100 according to the present invention includes an engine EN, a generator GE, a heating device HT, a heat storage tank WT, a cooling water circulation pipe 110, A waste heat recovery heat exchanger 120, a heater 130, a direct water pipe 140a, and a water discharge pipe 140b.

In addition, the present invention may be applied to a refrigeration system including a cooling device CL, a cooling heat exchanger 150, an exhaust pipe 160, a heating medium circulation pipe 170, a discharge pipe 180, and an exhaust heat recovery heat exchanger 190 .

The present invention relates to m-CHP (micro-combined heat and power), which is also used in domestic and industrial applications, and is an m-CHP device including an engine EN, a generator GE, and a waste heat recovery heat exchanger 120 To the heating device HT and the heat storage tank WT. Further, a hybrid system is constructed by further including a cooling device (CL).

Therefore, the engine EN and the generator GE are driven to generate electricity, and the generated electricity is supplied to the electric power load (electric load). In addition, waste heat is recovered in the process of cooling the engine EN and the generator GE while being driven, and the waste heat is stored in the heat storage tank WT through the heat recovery heat exchanger 120.

The hot water stored in the thermal storage tank WT is supplied to the heating device HT to be used for heating (or hot water supply). Further, if necessary, the medium-temperature water stored in the thermal storage tank WT is supplied to the cooling device CL and is also used as a driving heat source for the cooling device CL.

In particular, the present invention is adaptively operated according to a load. In the case where there is no power load or underload, the heater 130 consumes power in the system 130, thereby heating the water in the storage tank with the heater 130.

Further, in the case where there is no heating load (including a cooling load in the presence of a cooling device), the present invention discharges warm water stored in the water discharge pipe 140b while replenishing the direct water at a low temperature with the direct water pipe 140a, It enables continuous operation.

That is, the heater 130 of the present invention is adaptively operated according to the load, and the direct water pipe 140a and the water discharge pipe 140b are adaptively opened and closed according to the load, .

As a preferred embodiment of the present invention, the present invention is characterized in that high temperature exhaust gas generated during driving of the engine EN is recovered in the heat exchanger 150 for cooling and used as a heat medium serving as a driving heat source of the cooling device CL, The waste heat is further recovered in the exhaust heat recovering heat exchanger 190 and transferred to the waste heat recovering heat exchanger 120.

As described above, the present invention supplies heating (or hot water) together with power generation, and also supplies cooling medium to cooling device CL to supply cooling medium. Thus, the cooling heat is also supplied to the recovered waste heat in addition to the heating, thereby improving the COP (coefficient of performance) of the cooling system CL.

Further, as described in more detail below, it is possible to select one of the operation modes of heating, power, cooling, heating, power, cooling and power load according to the type of load in one system, .

For this purpose, the engine EN is a power generation drive apparatus such as a gas engine or a Stirling engine. In this case, when a gas engine EN is used as an internal combustion engine, combustion air and fuel gas supplied through the intake filter F And the fuel gas is supplied by mixing.

Then, the engine EN combusts the supplied mixed combustion gas, whereby the piston reciprocates along the four stroke cycle of suction, compression, explosion and exhaust as is well known and the crankshaft operates.

In this way, the electricity generated by the generator GE by operating the generator GE is supplied to the electric distribution panel through an inverter or the like. The power provided to the electric distribution panel is supplied to the power load (PWR).

Meanwhile, in order to continuously operate the engine EN and the generator GE, cooling water is used to prevent overheating. At this time, the cooling water collects the waste heat in the process of cooling the engine EN and the generator GE, .

A water jacket installed in the engine EN or the generator GE can be used as it is for cooling the engine EN and recovering the waste heat of the generator GE. Instead of the water jacket or a separate water jacket, a separate heat exchanger tube (not shown) may be used to enclose the surface of the engine EN in the direction of the jig.

Next, the heating device HT supplies heating or hot water to the load side, and the heating device HT supplies cooling and heating to the load side using waste heat (i.e., medium temperature water) stored in the heat storage tank WT.

The heating device HT includes various loads including a radiator and the like in addition to the floor heating, and the heating device HT here also includes a hot water supply device. That is, the heating load also includes hot water supply.

The cooling device CL supplies cooling to the load side, and the cooling device CL also supplies cooling to the load side by using waste heat accumulated in the heat storage tank WT.

Particularly, the cooling device CL is a hybrid absorption refrigerator, and in this case, the heat medium which exchanges heat with the high temperature exhaust gas generated in the engine EN is steam. Therefore, a 'steam heat exchanger' is used as the cooling heat exchanger 150.

Accordingly, the present invention improves the energy efficiency by improving the COP, which represents the ratio of the refrigerating capacity in the refrigerating cycle to the consumption amount of the consumed compressor, by supplying the heating medium to the cooling device CL.

The heat storage tank WT collects and accumulates waste heat generated when the engine EN and the generator GE are driven. The heat storage is performed by a method of storing the medium temperature water, and is performed by the cooling water system and the heating medium (ie, steam) system.

The heat stored in the cooling water system is transferred to the waste heat recovery heat exchanger 120 through the waste heat recovered in the process of cooling the generator GE and the engine EN by the cooling water. In the case of including the exhaust heat recovering heat exchanger 190, waste heat is recovered in the exhaust heat recovering heat exchanger 190 as well.

When the heating medium is not used in the cooling device CL, heat storage in the heating medium system is performed by supplying the heating medium to the heat storage tank WT instead of the cooling device CL and recovering the waste heat by heating the water.

The cooling water circulation pipe 110 recovers the waste heat of the engine EN and the generator GE in the process of cooling the engine EN and the generator GE by circulating the cooling water. Also, waste heat of the exhaust gas supplied to the exhaust heat recovering heat exchanger 190 is also recovered.

The waste heat recovered through the cooling water circulation pipe (110) is transferred to the waste heat recovery heat exchanger (120). To this end, the cooling water circulation pipe (110) recovers the waste heat and supplies the cooling water whose temperature has risen to the primary side of the waste heat recovery heat exchanger (120).

The cooling water circulation pipe 110 is connected to the waste heat recovery heat exchanger 120 through the exhaust heat recovery heat exchanger 190, the generator GE and the engine EN. Therefore, the cooling water circulates on the primary side of the exhaust heat recovery heat exchanger 190, the generator GE, the engine EN, and the waste heat recovery heat exchanger 120.

Particularly, the cooling water circulates sequentially through the exhaust heat recovering heat exchanger 190, the generator GE and the engine EN in the order of low temperature of the waste heat, thereby recovering the maximum amount of heat and increasing the thermal efficiency.

The waste heat recovery heat exchanger 120 is for heating the water stored in the heat storage tank WT using the waste heat recovered by the cooling water. The cooling water supplied from the cooling water circulation pipe 110 passes through the primary side, (WT) is passed through.

The waste heat recovery heat exchanger 120 is a water-to-water heat exchanger. Various heat exchangers such as a plate heat exchanger are used. The waste heat recovered from the cooling water is transferred to the heat storage tank WT as described above.

For this purpose, the cooling water circulation pipe 110 is connected to the primary side of the waste heat recovery heat exchanger 120. The secondary side of the waste heat recovery heat exchanger 120 is connected to the storage heat transfer pipe RP and the heat storage supply pipe SP and is piped so as to circulate the inside of the heat storage tank WT.

The heater 130 heats the water in the heat storage tank WT and is electrically connected to the output terminal of the generator GE to receive power from the generator GE.

The heater 130 of the present invention activates the electric furnace heater 130 generated by the generator GE in the absence of a power load and further heats the water of the storage tank WT by the heat generated by the heater 130, .

As described above, the present invention can be applied to a 'load adaptive type' in that it operates the heater 130 adaptively according to the state of the load, such as when there is a power load, and conversely, when there is no power load System.

1 to 5, the heater 130 is disposed on the relatively low temperature side heat storage and return pipe RP. However, the heater 130 may be installed directly inside the heat storage tank WT in addition to the heat storage and return pipe RP It will be self-evident.

The direct water pipe 140a and the water discharge pipe 140b prevent the water temperature of the heat storage tank WT from excessively increasing in the case where there is only a power load without heating load (no cooling load is added when a cooling device is added) It enables continuous development while cooling.

To this end, the direct water pipe 140a supplies low-temperature direct water to the secondary side of the waste heat recovery heat exchanger 120, and the water discharge pipe 140b is configured to discharge the hot water stored in the heat storage tank WT to the outside of the system.

Therefore, when the temperature of the water filled in the heat storage tank WT excessively rises, water is discharged through the water discharge pipe 140b, and water of low temperature is supplied through the water discharge pipe 140a to pass through the waste heat recovery heat exchanger 120 Lower the temperature of the cooling water.

If the temperature of the cooling water is prevented from excessively increasing, cooling of the engine (EN) and the generator (GE) with cooling water of a suitably lower temperature enables the continuous development of the load adaptive cogeneration system.

As described above, according to the present invention, in addition to the case where the heater 130 is adaptively operated, when there is no heating load (or heating load and cooling load) and conversely there is a heating load (or heating load and cooling load) And controls the direct water pipe 140a and the water discharge pipe 140b adaptively in accordance with the load condition as well.

The control of the direct water pipe 140a and the water discharge pipe 140b may be performed by a method of controlling the opening and closing of the direct water pipe 140a and the water discharge pipe 140b using a typical electric valve, ) Processes the process automatically.

On the other hand, in the cooling heat exchanger 150, heat exchange is performed between the high temperature exhaust gas discharged from the engine EN and a heating medium (for example, steam) for driving the cooling device CL.

To this end, the exhaust pipe 160 guides the high-temperature exhaust gas discharged from the engine EN to the outside after passing through the primary side of the heat exchanger 150 for cooling.

The heat medium circulation pipe 170 is connected to the secondary side of the cooling heat exchanger 150 and the cooling device CL such that the heat medium having the increased temperature is circulated through the cooling device CL after the heat exchange in the cooling heat exchanger 150 is completed Connect.

Therefore, heat exchange is performed between the high-temperature exhaust gas flowing in the primary side inside the cooling heat exchanger 150 and the heat medium flowing in the secondary side, and the heat medium collects the heat and becomes high-temperature steam.

Preferably, the heating medium, which has been heat-exchanged in the cooling heat exchanger 150 and has a raised temperature, is circulated to the cooling device CL or circulated through the heat storage tank WT by the heat medium circulation pipe 170.

The heat medium circulation pipe 170 is connected to the first heat medium circulation pipe 171 for circulating the cooling heat exchanger 150 and the cooling device CL between the cooling heat exchanger 150 and the heat storage tank WT And a three-way valve 173 installed in a branch passage connecting the first heat medium circulation pipe 171 and the second heat medium circulation pipe 172 to each other.

Therefore, the heating medium is supplied to the cooling device CL via the first heating medium circulation pipe 171 to operate the cooling device CL, or the heating medium is supplied to the heat storage tank WT through the second heating medium circulation pipe 172 And the water in the heat storage tank WT is heated.

A muffler M is installed downstream of the exhaust pipe 160 to reduce noise and the like. Particularly, the exhaust pipe 160 is connected to a primary side of an exhaust heat recovery heat exchanger 190 to be described later, Heat exchange.

The discharge pipe 180 supplies the intermediate water stored in the heat storage tank WT to the heating device HT and is connected to the heat storage tank WT at one end and to the heating device HT at the other end. The medium temperature water supplied to the heating device (HT) is used for heating or hot water supply.

In particular, when the cooling device CL is also applied to the present invention, the branch discharge pipe 180 is used as the discharge pipe 180. At this time, the first discharge end of the branch type discharge pipe 180 is connected to the heating device HT, and the second discharge end is connected to the cooling device CL so that the middle temperature water can be supplied to the air conditioner CL in addition to the heating device HT. .

As described above, the cooling apparatus CL according to the present invention is characterized in that the COP is improved as described above by using the absorption type refrigerator, which is a hybrid system driven by using the medium temperature water of the heat storage tank (WT) in addition to the heating medium, that is, steam.

In the exhaust heat exchanger 190, heat exchange is performed between the high temperature exhaust gas discharged from the engine EN and the cooling water. The exhaust heat recovery efficiency of the exhaust gas can be further improved by additionally providing such an exhaust heat recovery heat exchanger (190).

Particularly, the exhaust heat recovering heat exchanger 190 is connected to the exhaust end of the cooling heat exchanger 150 so that the exhaust gas that has undergone the heat exchange in the first order in the cooling heat exchanger 150 can perform heat exchange in the second order.

The cooling water circulation pipe 110 is arranged such that the cooling water circulates through the exhaust heat recovery heat exchanger 190, the generator GE, the engine EN and the waste heat recovery heat exchanger 120 in sequence And is piped to circulate.

Hereinafter, the load adaptive cogeneration system according to the present invention constructed as described above will be divided into the load types. 1 to 5, which will be described below, represent heating, power, cooling, heating, power, cooling, and power loads, respectively.

First, Fig. 1 shows a case where there is only a heating load. For heating, the medium temperature water is sufficiently supplied to the heat storage tank WT, and the generated electricity is used in the heater 130 instead of the load.

To this end, when the generator GE is activated by the engine EN, electricity is produced, and the produced electricity is supplied to the heater 130 through the distribution board, so that electricity generated at the present time can be consumed by the heater 130 . Thus, energy efficiency is enhanced.

The cooling water is recovered from the waste heat while passing through the exhaust heat recovery heat exchanger 190, the generator GE and the engine EN by the cooling water circulation pipe 110. The recovered waste heat is stored in the heat storage tank (WT) via the waste heat recovery heat exchanger (120).

The medium-temperature water stored in the heat storage tank WT is supplied to the heating device HT through the discharge pipe 180 to supply hot water or heating water to the load.

At the same time, the high-temperature exhaust gas generated in the engine EN is supplied to the cooling heat exchanger 150 to heat the heating medium. The heated heating medium is supplied to the heat storage tank WT through the three-way valve 133 and the second heat medium circulation pipe 172, for example.

At this time, the heating medium is directly injected into the heat storage tank WT without a separate heat exchanger, or indirectly exchanged through a heat exchanger (not shown) provided inside the heat storage tank WT, Further heating.

The exhaust gas, which has undergone the primary heat exchange in the cooling heat exchanger (150), exchanges heat with the cooling water as described above in the process of being exhausted through the exhaust heat exchanger (190).

When there is only the heating load as described above, the middle-temperature water is not supplied to the cooling system CL through the discharge pipe 180, and the direct water pipe 140a and the water discharge pipe 140b are also closed. On the other hand, the heater 130 is turned on. That is, the heater 130 is turned on or off depending on the power load.

Next, Fig. 2 shows a case where there is only a power load. If there is a power load, the developed electricity is used in the same power load as the consumer.

That is, when the generator EN is activated by the engine EN, electricity is produced, and the produced electricity is supplied to the power load side such as a consumer through the distribution board.

The cooling water is recovered from the waste heat while passing through the exhaust heat recovery heat exchanger 190, the generator GE and the engine EN by the cooling water circulation pipe 110. The recovered waste heat is temporarily stored in the heat storage tank (WT) via the waste heat recovery heat exchanger (120).

At the same time, the high-temperature exhaust gas generated in the engine EN is supplied to the cooling heat exchanger 150 to heat the heating medium. The heated heating medium is supplied to the heat storage tank WT through the three-way valve 133 and the second heat medium circulation pipe 172, for example.

The exhaust gas that has undergone the primary heat exchange in the cooling heat exchanger 150 is subjected to heat exchange with the cooling water in the process of being exhausted through the exhaust heat exchanger 190 so that the waste heat is temporarily stored in the heat storage tank WT .

However, when the waste heat is recovered and the waste heat is continuously stored in the heat storage tank WT, the temperature of the cooling water is increased through the waste heat recovery heat exchanger 120, thereby preventing overheating of the generator GE and the engine EN.

The low temperature direct water is supplied to the waste heat recovering heat exchanger 120 through the direct water pipe 140a and at the same time or at a high temperature which is filled in the heat storage tank WT according to the hot water temperature inside the heat storage tank WT, To the outside of the system through the water discharge pipe 140b. The hot water discharged can be used in other systems or simply discarded.

If there is only the power load as described above, the middle temperature water is not supplied to the cooling device CL and the heating device HT through the discharge pipe 180, and the heater 130 is turned off. On the other hand, the direct water pipe 140a and the water discharge pipe 140b are opened. That is, the direct water pipe 140a and the water discharge pipe 140b are opened or closed depending on the load.

Next, FIG. 3 shows a case where there is only a cooling load. In order to perform cooling, a heating medium or medium temperature water is supplied to the cooling system CL, and the generated electricity is used in the heater 130 instead of the load.

When the generator EN is operated by the engine EN, electricity is produced. The generated electricity is supplied to the heater 130 through the distribution board, and the heater 130 supplies water filled in the heat storage tank WT Heat it. That is, when the power load is absent or the load is insufficient, the heater 130 consumes electricity generated in the past.

The cooling water is recovered from the waste heat while passing through the exhaust heat recovery heat exchanger 190, the generator GE and the engine EN by the cooling water circulation pipe 110. The recovered waste heat is stored in the heat storage tank (WT) via the waste heat recovery heat exchanger (120).

The warm water stored in the heat storage tank WT is supplied to the hybrid cooling apparatus CL such as the absorption type refrigerator and used as a driving source of the cooling apparatus CL.

At the same time, the high-temperature exhaust gas generated in the engine EN is supplied to the cooling heat exchanger 150 to heat the heating medium. The heating medium heated through the heat exchange is supplied to the cooling device CL through the first heating medium circulation pipe 171.

The exhaust gas, which has undergone the primary heat exchange in the cooling heat exchanger (150), exchanges heat with the cooling water as described above in the process of being exhausted through the exhaust heat exchanger (190).

When there is only a cooling load as described above, the middle-temperature water is not supplied to the heating device HT through the discharge pipe 180, and the direct water pipe 140a and the water discharge pipe 140b are also closed. On the other hand, the heater 130 is turned on as described above.

Next, FIG. 4 shows a case where there is heating and power load. For heating, the warm water should be supplied to the heat storage tank (WT) sufficiently, and the developed electricity should be supplied and used to the load side.

To this end, electricity is produced when the generator (GE) is activated by the engine (EN), and the produced electricity is supplied to the power load side such as a consumer through the distribution board.

The cooling water is recovered from the waste heat while passing through the exhaust heat recovery heat exchanger 190, the generator GE and the engine EN by the cooling water circulation pipe 110. The recovered waste heat is stored in the heat storage tank (WT) via the waste heat recovery heat exchanger (120).

The medium-temperature water stored in the heat storage tank WT is supplied to the heating device HT through the discharge pipe 180 to supply hot water or heating water to the load.

At the same time, the high-temperature exhaust gas generated in the engine EN is supplied to the cooling heat exchanger 150 to heat the heating medium. The heating medium heated through heat exchange is supplied to the heat storage tank WT through the three-way valve 133 and the second heat medium circulation pipe 172, for example.

At this time, the heating medium is directly injected into the heat storage tank WT without a separate heat exchanger, or indirectly heat exchanged through a heat exchanger (not shown) provided inside the heat storage tank WT, thereby adding water in the heat storage tank WT .

The exhaust gas, which has undergone the primary heat exchange in the cooling heat exchanger (150), exchanges heat with the cooling water as described above in the process of being exhausted through the exhaust heat exchanger (190).

When there is only the heating and power load as described above, the medium temperature water is not supplied to the cooling system CL through the discharge pipe 180 and the heater 130 is in the off state, and the direct water pipe 140a and the water discharge pipe 140b are closed State.

Next, FIG. 5 shows a case where cooling and power loads are present. For cooling, a heating medium or medium temperature water is supplied to the cooling system (CL), and the generated electricity should be supplied to the load side and used.

To this end, when the generator EN is activated by the engine EN, electricity is produced, and the produced electricity is supplied to the power load side PWR such as a consumer through the distribution board.

The cooling water is recovered from the waste heat while passing through the exhaust heat recovery heat exchanger 190, the generator GE and the engine EN by the cooling water circulation pipe 110. The recovered waste heat is stored in the heat storage tank WT through the waste heat recovery heat exchanger 120 (that is, generated in the medium temperature water).

The warm water stored in the heat storage tank WT is supplied to the hybrid cooling apparatus CL such as the absorption type refrigerator and used as a driving source of the cooling apparatus CL.

At the same time, the high-temperature exhaust gas generated in the engine EN is supplied to the cooling heat exchanger 150 to heat the heating medium. The heated heating medium (i.e., steam) is supplied to the cooling device CL through the first heating medium circulation pipe 171.

The exhaust gas, which has undergone the primary heat exchange in the cooling heat exchanger (150), exchanges heat with the cooling water as described above in the process of being exhausted through the exhaust heat exchanger (190).

When there is only cooling and power load as described above, the middle temperature water is not supplied to the heating device HT through the discharge pipe 180, the heater 130 is in the off state, and the direct water pipe 140a and the water discharge pipe 140b are closed State.

Hereinafter, a load adaptive cogeneration system according to another embodiment of the present invention will be described with reference to the accompanying drawings.

6 and 7 are diagrams showing a load-adaptive cogeneration system according to another embodiment of the present invention. FIG. 6 is a diagram showing a fourth operation mode (heating + power load) FIG.

6 and 7, another embodiment of the present invention includes an engine EN, a generator GE, a heat storage tank WT, a cooling water circulation pipe 110, a waste heat recovery heat exchanger 120, a direct water pipe 140a, And a water discharge pipe 140b.

Further, it further includes a cooling device CL, a cooling heat exchanger 150, an exhaust pipe 160, a heating medium circulation pipe 170, a discharge pipe 180 and an exhaust heat recovering heat exchanger 190, The heater 130 and the heating device HT are also included.

This is the same as the load adaptive cogeneration system according to the embodiment of the present invention described above with reference to Figs. 1 to 5 above.

However, in another embodiment of the present invention, the intermediate-temperature water storage tank WT-1 and the steam storage tank WT-2 are provided as the heat storage tank WT so as to separate and circulate the two heat storage media including the intermediate- There is a difference.

The waste heat recovery heat exchanger 120 is provided with a first waste heat recovery heat exchanger 120-1 and a second waste heat recovery heat exchanger 120-2 so that the above described warm water is supplied to the intermediate temperature water storage heat exchanger WT- (CL), and circulates the refrigerant.

As shown in FIGS. 1 to 5, when a single integrated heat storage tank WT is used, the thermal efficiency is relatively low, and a complex coil configuration for middle temperature water and steam is not easy due to the internal temperature distribution.

In addition, when the integrated waste heat recovery heat exchanger 120 is used, the generated warm water is supplied to the cooling system CL through the heat storage tank WT, so that the efficiency is lowered and a temperature drop due to the heat loss occurs.

However, by providing the intermediate-temperature water storage tank WT-1 and the steam storage tank WT-2 separated from each other as shown in FIGS. 6 and 7, it is possible to provide the optimum thermal efficiency for each heat medium, .

The first waste heat recovering heat exchanger 120-1 and the second waste heat recovering heat exchanger 120-2 which are separated from each other are provided with cooling devices for circulation and cooling of the intermediate temperature water storage heat exchanger WT- CL) circulation to increase efficiency and prevent temperature drop.

More specifically, the cooling device CL applied to the present invention is applied to a double effect absorption type refrigerator which is driven by steam and two kinds of medium-temperature water.

The double-effect absorption refrigerator itself is already known, and the single-use system using only the middle temperature of about 80 ° C to 120 ° C has a COP of about 0.7, whereas the double-effect system has a high COP of about 1.2.

Such a dual efficiency system includes a high temperature generator using a regeneration system of refrigerant (i.e., medium pressure steam) in a refrigerant cycle and a low temperature generator using medium temperature water, so that steam and medium temperature water are independently supplied as a heating medium as follows.

To this end, the heat storage tanks WT include a medium-temperature water storage tank WT-1 and a steam storage tank WT-2 which are independently provided. The waste heat recovery heat exchanger 120 includes a first waste heat recovery heat exchanger 120-1 and a second waste heat recovery heat exchanger 120-2 that are provided independently of each other.

At this time, the heater 130 is installed on the secondary side of the first waste heat recovery heat exchanger 120-1 to heat the water in the intermediate-temperature water storage tank WT-1. That is, the adaptive operation according to the load can be applied to the intermediate-temperature water storage heat exchanger (WT-1).

The primary side of the first waste heat recovering heat exchanger 120-1 is connected to the cooling water circulation pipe 110 through the cooling water circulation pipe 110 and the secondary side through the water of the intermediate- Water heat exchange is performed.

The cooling water supplied from the cooling water circulation pipe 110 passes through the primary side of the second waste heat recovery heat exchanger 120-2 and the secondary side passes through the pipe Water-to-water heat exchange takes place.

Preferably, the three-way valve 111 is added to the cooling water circulation pipe 110 so that the cooling water circulates through the first waste heat recovery heat exchanger 120-1 and / or the second waste heat recovery heat exchanger 120-2, Adjust the cycle.

Therefore, heat exchange is performed in the first waste heat recovery heat exchanger 120-1 by the waste heat recovered in the cooling water cooling process of the engine EN and the generator GE, and the generated intermediate-temperature water is supplied to the intermediate-temperature water storage heat exchanger WT -1). The regenerated medium temperature water is used for heating.

On the other hand, as described above, heat exchange is performed in the second waste heat recovery heat exchanger 120-2 with the waste heat recovered from the cooling water, and the generated intermediate-temperature water is supplied to the intermediate-temperature water receiving portion of the cooling device CL, Temperature generator.

Further, the heat medium used in the cooling heat exchanger 110 is steam, and the cooling heat exchanger 110 is a steam heat exchanger using steam.

At this time, the heat medium circulation pipe 170 includes a first heat medium circulation pipe 171 for circulating between the cooling heat exchanger 110 and the cooling device CL, a cooling heat exchanger 110 and a steam storage tank WT- And a three-way valve 173 installed in a branch path connecting the first heat medium circulation pipe 171 and the second heat medium circulation pipe 172. The three-way valve 173 is connected to the first heat medium circulation pipe 171 and the second heat medium circulation pipe 172.

Accordingly, the steam is supplied to the steam receiving portion of the cooling device CL through the first heat medium circulation pipe 171 to operate the cooling device CL, or steam is supplied to the second heat medium circulation pipe 172 through the second heat medium circulation pipe 172 Is supplied to the second storage tank WT-2 to heat the water in the second storage tank WT-2.

Another embodiment of the present invention also includes an arrangement recovery heat exchanger 190 and includes a direct water pipe 140a, a water discharge pipe 140b and a heating device HT, As shown in FIG.

Particularly, since the recovered waste heat is stored in each of the intermediate-temperature water storage tank WT-1 and the steam storage tank WT-2, the heating device HT is disposed in the intermediate temperature water storage tank WT-1 and the steam storage tank WT- The heating water can be supplied from any one or more of the heating units to supply the heating.

6 shows the heating + power load, and FIG. 7 shows the cooling + power load. However, another embodiment of the present invention is also applicable to the heating load, the power load And a cooling load.

The specific embodiments of the present invention have been described above. It is to be understood, however, that the scope and spirit of the present invention is not limited to these specific embodiments, and that various modifications and changes may be made without departing from the spirit of the present invention. If you have, you will understand.

Therefore, it should be understood that the above-described embodiments are provided so that those skilled in the art can fully understand the scope of the present invention. Therefore, it should be understood that the embodiments are to be considered in all respects as illustrative and not restrictive, The invention is only defined by the scope of the claims.

EN: Engine
GE: generator
CL: Air conditioner
HT: Heating
WT (WT-1, WT-2): Heat storage tank
110: Cooling water circulation pipe
120 (120-1, 120-2): waste heat recovery heat exchanger
130: heater
140a: direct water pipe
140b: drainage pipe
150: Heat exchanger for cooling
160: Exhaust pipe
170: Heat medium circulation tube
180: discharge pipe
190: Array recovery heat exchanger

Claims (6)

An engine EN;
A generator GE driven by the engine EN to produce electricity;
A heating device HT for supplying heating or hot water to the load side;
A heat storage tank (WT) for storing hot water and supplying the hot water to the heating device;
A cooling water circulation pipe (110) circulating the cooling water to collect waste heat in a process of cooling while passing through the generator (GE) and the engine (EN);
A waste heat recovering heat exchanger 120 for passing the cooling water supplied from the cooling water circulation pipe 110 to the primary side and water-to-water heat exchange by passing water of the storage tank WT on the secondary side;
A heater 130 for heating water in the thermal storage tank WT;
A direct water pipe 140a for supplying low-temperature direct water to the secondary side of the waste heat recovery heat exchanger 120; And
And a water discharge pipe (140b) for discharging hot water stored in the thermal storage tank (WT) to the outside of the system,
The heater 130 is electrically connected to receive the electric power of the generator GE. When the electric load is absent or is insufficient, the heater 130 is operated by electricity generated from the electric generator GE, ) Was heated,
The low temperature direct water is supplied through the direct water pipe 140a and the high temperature water stored in the heat storage tank WT is discharged to the engine EN and the electric generator GE, So that continuous power generation can be achieved without overheating the load-adaptive cogeneration system. delete The method according to claim 1,
A cooling device CL for supplying cooling to the load side;
A cooling heat exchanger (150) for performing heat exchange between a high temperature exhaust gas discharged from the engine (EN) and a heat medium for driving the cooling device (CL);
An exhaust pipe 160 for guiding the high temperature exhaust gas discharged from the engine EN through the cooling heat exchanger 150 to be discharged to the outside;
A heating medium circulation pipe 170 for circulating the heat-exchanged heat medium in the cooling heat exchanger 150 to either the cooling device CL or the heat storage tank WT; And
And a discharge pipe (180) for supplying hot water stored in the thermal storage tank (WT) to either the heating device (HT) or the cooling device (CL)
When there is no heating load by the heating device HT and a cooling load by the cooling device CL, low-temperature direct water is supplied through the direct water pipe 140a, and high-temperature water stored in the heat storage tank WT is discharged Wherein the load-adaptive cogeneration system is a load-compatible cogeneration system. The method of claim 3,
The discharge pipe 180 is connected to the heating device HT via a branch discharge pipe 180 and the second discharge end is connected to the cooling device CL to supply hot water stored in the thermal storage tank WT To the heating device (HT) or the cooling device (CL). The method of claim 3,
The thermal storage tank WT includes a warm water storage tank WT-1 and a steam storage tank WT-2,
The waste heat recovery heat exchanger (120) includes a first waste heat recovery heat exchanger (120-1) and a second waste heat recovery heat exchanger (120-2) installed independently of each other,
Wherein the heater (130) is installed on a secondary side of the first waste heat recovery heat exchanger (120-1) to heat water in the intermediate temperature water storage tank (WT-1). 6. The method of claim 5,
The cooling device (CL) is a dual efficiency absorption type refrigerator driven by two heating media including steam and middle-temperature water,
The heating medium is steam,
The cooling heat exchanger 150 is a steam heat exchanger,
The cooling water supplied from the cooling water circulation pipe 110 passes through the primary side of the first waste heat recovery heat exchanger 120-1 and the secondary side is piped so that the water of the intermediate temperature water storage tank WT- Water-to-water heat exchange takes place,
The cooling water supplied from the cooling water circulation pipe 110 passes through the primary side of the second waste heat recovery heat exchanger 120-2 and the water supplied to the middle temperature water storage portion of the cooling device CL Water-to-water heat exchange takes place,
The heat medium circulation pipe 170 includes a first heat medium circulation pipe 171 circulating between the cooling heat exchanger 150 and the cooling device CL; A second heat medium circulation pipe 172 for circulating the cooling heat exchanger 150 and the steam storage tank WT-2; And a three-way valve (173) provided in a branch path connecting the first heat medium circulation pipe (171) and the second heat medium circulation pipe (172)
The steam is supplied to the steam accommodating portion of the cooling device CL through the first heat medium circulation pipe 171 to operate the cooling device CL or the steam is supplied to the second heat medium circulation pipe 172 Is supplied to the second heat storage tank (WT-2) through the second heat storage tank (WT-2) to heat the water in the second heat storage tank (WT-2).

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