KR20120136366A - Exhaust heat recovery power generation device and vessel provided therewith - Google Patents

Abstract

Provided is a heat recovery power generation apparatus capable of making an arrangement of engine coolant, which has a lower temperature level than the exhaust gas of an internal combustion engine, and has a low utilization value as a heat source of an organic Rankine cycle. A heat recovery recovery path 7 for recovering heat from the jacket cooling water for cooling the cylinder jacket 2 of the diesel engine and a first air cooler 5 for cooling the compressed air discharged from the supercharger of the diesel engine; Generated by the rotary output of the power turbine 32 and the power turbine 32 driven by the organic fluid evaporated by the evaporator 30, the evaporator 30 for evaporating the organic fluid by the recovered heat recovered in the present invention. The generator 38 and the condenser 36 which condenses the organic fluid which passed through the power turbine 32 are provided.

Description

Waste heat recovery power generation apparatus and ship equipped with this {EXHAUST HEAT RECOVERY POWER GENERATION DEVICE AND VESSEL PROVIDED THEREWITH}

The present invention relates to a heat recovery power generation apparatus for recovering and generating an array of an internal combustion engine, and a vessel provided with the same.

Background Art Conventionally, various techniques for recovering and generating an array of exhaust gas and the like of an internal combustion engine have been proposed. Patent Literature 1 below discloses a heat recovery and power generation apparatus that is generated by an organic Rankine cycle using an arrangement from a diesel generator as a heat source.

The document mainly describes heat recovery from exhaust gas of a diesel generator, and also shows that in the case of a water-cooled diesel engine, the engine cooling water (jacket cooling water) can be used.

Japanese Utility Model Registration No. 3044386 ([0010])

However, the engine cooling water has a problem that the temperature level is only 80 to 90 ° C, and the temperature level is low as a heat source for driving the organic Rankine cycle.

On the other hand, in the diesel engine used as a ship main vessel, a steam turbine and a power turbine (gas turbine) are examined as heat recovery of exhaust gas, and there are also the results which have already achieved predetermined efficiency. Therefore, using the exhaust gas of a ship cycle as a heat source of an organic Rankine cycle is not necessarily a benefit in achieving high efficiency heat recovery.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and has a heat recovery power generation apparatus capable of making an arrangement of engine coolant, which has a lower temperature level than the exhaust gas of an internal combustion engine and has a low utilization value, as a heat source for an organic Rankine cycle, and the same. The purpose is to provide a vessel.

In order to solve the said subject, the heat recovery power generation apparatus of this invention and the ship provided with this employ | adopt the following means.

That is, the heat recovery power generation apparatus according to the first aspect of the present invention includes an heat recovery recovery path for heat recovery in an engine coolant cooling the internal combustion engine body and an air cooler cooling the compressed air discharged from the supercharger of the internal combustion engine, and the arrangement thereof. An evaporator for evaporating the organic fluid by the recovery heat recovered in the recovery path, a turbine driven by the organic fluid evaporated by the evaporator, a generator generated by the rotational output of the turbine, and the organic matter passing through the turbine And a condenser for condensing the fluid.

The organic fluid is evaporated in an evaporator and then expanded in a turbine to carry out a cycle of condensation in the condenser, i.e., an Organic Rankine Cycle. In the present invention, the heat recovered from the engine cooling water and the air cooler is used as the heat source of the organic Rankine cycle. Thus, instead of using exhaust gas of an internal combustion engine having a high temperature level such as, for example, 250 ° C. or higher, engine coolant (for example, 80 to 90 ° C.) that has not been effectively used because the temperature level is lower than exhaust gas, and An air cooler (for example, 130-140 degreeC) can be used. In particular, as the temperature level of the heat source for driving the organic Rankine cycle is low only with the engine cooling water, heat recovery is also performed from the air cooler, thereby improving the feasibility of generating power by the organic Rankine cycle.

As an internal combustion engine, a marine diesel engine (cycle) is typically mentioned. However, the internal combustion engine for land use used for power generation etc. may not be limited to a ship.

It is preferable to perform heat recovery from an air cooler from the upstream (high temperature side) of compressed air.

As engine cooling water, the jacket cooling water which distributes the cylinder jacket of an internal combustion engine main body is typically mentioned.

Moreover, in the heat recovery power generation apparatus according to the first aspect, the heat recovery path includes a first heat recovery unit that performs heat exchange with the engine cooling water, and a second heat recovery unit as the air cooler. And the heat recovery medium heat-recovered in the recoverer and the second heat recoverer exchange heat with the organic fluid in the evaporator.

After the heat recovery medium (e.g. water) flowing through the heat recovery path recovers the heat from the engine coolant in the first heat recoverer and further recovers the heat from the compressed air in the second heat recoverer, the organic fluid is evaporated in the evaporator. It was supposed to be. In this way, since the heat recovery medium heat-recovered from the engine cooling water and the compressed air is directly guided to the evaporator without any other fruit, the heat of recovery can be led to the evaporator with little heat loss.

Moreover, in the heat recovery power generation apparatus according to the first aspect, the heat recovery recovery path is a third air cooler that performs heat exchange between the engine coolant and the compressed air while using the engine coolant as the heat recovery recovery medium. And an engine recovery water heat-recovered by the third array recovery device, and heat exchange with the organic fluid in the evaporator.

After the engine coolant flowing in the heat recovery path recovers the heat from the air cooler in the third heat recoverer, the organic fluid is evaporated in the evaporator. In this way, since the engine cooling water flowing through the heat recovery path is used as the heat recovery medium, a heat exchanger (first heat recovery device of the present invention) that exchanges heat with the engine coolant can be omitted, and a simplified structure can be realized. In addition, since the engine cooling water recovered from the air cooler is directly guided to the evaporator without any other fruit, the heat of recovery can be led to the evaporator with little heat loss.

Moreover, in the heat recovery power generation apparatus according to the first aspect, the fruit is circulated, and the fruit recovery path includes a fruit circulation path in which the fruit heat exchanges with the organic fluid in the evaporator, and the heat recovery path passes heat exchange with the engine cooling water. A first heat recovery unit to be implemented, a second heat recovery unit as the air cooler, and a heat recovery unit heat-recovered by the first heat recovery unit and the second heat recovery unit exchange heat with the fruit of the fruit circulation path.

After the heat recovery medium flowing through the heat recovery path recovers the heat from the engine coolant in the first heat recoverer and further recovers the heat from the air cooler in the second heat recoverer, the fruit of the fruit circulation path (for example, water or fruit Heat exchange with oil). And the fruit which received the heat of recovery was made to evaporate an organic fluid in an evaporator. In this way, the heat of recovery may be induced into the organic fluid via the fruit circulation path.

Moreover, in the heat recovery power generation apparatus according to the first aspect, the fruit is circulated, and the fruit recovery path includes a fruit circulation path in which the fruit heat exchanges with the organic fluid in the evaporator. In addition to the medium, the engine coolant having a third heat recovery unit as the air cooler that performs heat exchange between the engine cooling water and the compressed air, and the engine coolant heat-recovered by the third heat recovery unit exchanges heat with the fruit of the fruit circulation path. Characterized in that.

After the engine coolant flowing in the heat recovery path recovers the heat from the air cooler in the third heat recovery machine, the engine cooling water is heat-exchanged with the fruit (for example, water or fruit oil) in the fruit circulation path. And the fruit which received the heat of recovery was made to evaporate an organic fluid in an evaporator. In this way, the heat of recovery may be induced into the organic fluid via the fruit circulation path.

In addition, since it is assumed that the engine cooling water flowing through the heat recovery path is used as the heat recovery medium, the heat exchanger (the first heat recovery device of the present invention) which exchanges heat with the engine coolant can be omitted, and a simplified structure can be realized.

Moreover, the heat recovery power generation apparatus according to the first aspect includes a steam turbine generator driven by steam generated by an exhaust gas heat exchanger that exchanges heat with exhaust gas of the internal combustion engine.

For example, the exhaust gas of an internal combustion engine having a high temperature level such as 250 ° C. or higher is supposed to be developed into a steam turbine which can be expected to have high efficiency. This enables heat recovery and generation with high efficiency over a wide temperature range.

Moreover, in the heat recovery power generation apparatus according to the first aspect, the exhaust gas heat exchanger includes an evaporation section for evaporating water and an overheating section for superheating steam generated in the evaporation section, wherein the heat recovery path is the above-mentioned. It is characterized by including the 4th heat recoverer which heat-exchanges with the steam obtained by the evaporation part.

In the fourth heat recovery unit, since the vapor obtained from the evaporation unit of the exhaust gas heat exchanger (exhaust gas economizer) is exchanged with the heat recovery medium, heat recovery can be performed more effectively.

Moreover, the heat recovery power generation apparatus according to the first aspect is provided with a gas turbine generator driven by exhaust gas of the internal combustion engine.

For example, the exhaust gas of an internal combustion engine having a high temperature level such as 250 ° C. or higher is supposed to be generated by a gas turbine (power turbine) capable of high efficiency. This enables heat recovery and generation with high efficiency over a wide temperature range.

Moreover, by combining with a steam turbine generator, it can be made more efficient.

Moreover, the ship which concerns on the 2nd aspect of this invention is equipped with any of the above-mentioned heat recovery power generation apparatuses, It is characterized by the above-mentioned.

Since the ship which concerns on the said 2nd aspect is equipped with any of the above-mentioned heat recovery power generation apparatuses, it can provide the ship with high energy saving which can effectively recover heat.

According to the present invention, the heat recovered by the engine cooling water and the air cooler is used as the heat source for driving the organic Rankine cycle. Thereby, electric power generation can be performed effectively utilizing the arrangement | positioning of the engine cooling water which was conventionally low in utility value.

BRIEF DESCRIPTION OF THE DRAWINGS The figure which shows roughly the heat recovery power generation apparatus which concerns on the 1st Embodiment of this invention.
2 is a diagram schematically showing a heat recovery power generation device according to a second embodiment of the present invention.
3 is a diagram schematically showing a heat recovery generator according to a third embodiment of the present invention.
4 is a diagram schematically showing a heat recovery power generation device according to a fourth embodiment of the present invention.
5 is a diagram schematically showing a heat recovery power generation device according to a fifth embodiment of the present invention.
6 is a diagram schematically showing a heat recovery generator according to a sixth embodiment of the present invention.

EMBODIMENT OF THE INVENTION Below, with respect to each embodiment which concerns on this invention, the heat recovery power generation apparatus is demonstrated with reference to drawings, taking as an example the structure provided as heat recovery of the propulsion cycle (diesel engine; internal combustion engine) of a ship.

[First Embodiment]

1, the heat recovery power generation apparatus according to the first embodiment of the present invention is schematically shown.

The heat recovery generator is discharged from a preheater (first heat recovery unit) 1 that recovers heat from a jacket cooling water (engine cooling water) flowing through a cylinder jacket 2 that cools a cylinder block of a diesel engine and the like, and a supercharger of a diesel engine. The first air cooler (2nd heat recovery machine) 5 which cools and heat-recovers the compressed air used, and the fruit water (array recovery medium) which receives an arrangement from these preheaters 1 and the 1st air cooler 5 are circulated. The heat recovery path 7 and the organic fluid path 9 which receive heat from the fruit water of the heat recovery path 7 and comprise an organic Rankine cycle are provided.

In addition, in FIG. 1, the area | region enclosed by the dashed-dotted line has shown the power generation apparatus 10 for organic Rankine cycles. For example, by installing this organic Rankine cycle power generation device 10 on an existing vessel, additional heat recovery can be easily added.

The jacket cooling water flowing in the cylinder jacket 2 circulates in the jacket cooling water circulation flow path 14 by the jacket cooling water pump 12. The jacket cooling water circulation passage 14 is formed such that the jacket cooling water flows in the order of the cylinder jacket 2, the preheater 1, the three-way valve 16 for temperature adjustment, and the jacket cooling water pump 12.

In the jacket cooling water circulation channel 14, a bypass channel 23 through which the jacket cooling water bypasses the preheater 1 is formed. The flow rate of the jacket cooling water flowing to the preheater 1 can be adjusted by adjusting the flow volume which flows through this bypass flow path 23 with the bypass valve which is not shown in figure.

The three-way valve 16 for temperature adjustment operates so that the jacket cooling water flowing into the cylinder jacket 2 may have a desired inlet temperature. Specifically, when the inlet temperature into which the jacket cooling water flows into the cylinder jacket 2 is higher than the set value, fresh water of about 30 ° C. derived from the second air cooler 18 is introduced into the jacket cooling water circulation flow path 14. It works to flow a lot.

On the upstream side of the three-way valve 16 for temperature adjustment, a branch flow passage 22 branched to the fresh water pump 20 is formed. The jacket cooling water flowing in the jacket cooling water circulation flow path 14 from this branch flow passage 22 is discharged to the fresh water pump 20 side, so that the mass balance of the circulation flow rate flowing in the jacket cooling water circulation flow path 14 is maintained.

The second air cooler 18 is provided downstream of the first air cooler 5 with respect to the flow of compressed air discharged from the supercharger. Therefore, the 1st air cooler 5 is provided so that temperature level may become higher than the 2nd air cooler 18. As shown in FIG.

Fresh water flowing in the second air cooler 18 is guided after being cooled by a central cooler (not shown). Part of the fresh water cooled by the second air cooler 18 in the compressed air is guided to the three-way valve 16 for temperature adjustment, and the remainder is returned to the central cooler by the fresh water pump 20.

Next, the heat recovery path 7 will be described.

The heat recovery path 7 is a closed circuit, and a heat recovery pump 24 for circulating the fruit water is formed. By this heat recovery pump 24, the fruit water circulates so as to exchange heat with the preheater 1, the first air cooler 5, and the evaporator 30.

The fruit water inlet temperature of the evaporator 30 becomes about 130-140 degreeC, for example. In this evaporator 30, the organic fluid is evaporated by the fruit water.

Next, the organic fluid path 9 will be described.

As the organic fluid flowing through the organic fluid path 9, low molecular hydrocarbons such as isopentane, butane and propane, R134a and R245fa used as a refrigerant can be used.

The organic fluid path 9 is a closed circuit, and a pump 31 for organic fluid for circulating the organic fluid is formed. The organic fluid circulates while repeating the phase change to pass through the evaporator 30, the power turbine 32, the economizer 34, and the condenser 36.

The power turbine 32 is rotationally driven by the thermal drop (enthalpy drop) of the organic fluid evaporated by the evaporator 30. The rotational power of the power turbine 32 is transmitted to the generator 38, and the electric power is obtained from the generator 38. The electric power obtained by the generator 38 is supplied to the system in ship through the electric power line which is not shown in figure.

The organic fluid (gas phase) which has completed the work in the power turbine 38 preheats the organic fluid (liquid phase) sent from the pump 31 for organic fluid in the economizer 34.

The organic fluid which has passed through the economizer 34 is cooled by seawater in the condenser 36 and condensed and liquefied. The condensed liquefied organic fluid is sent to the economizer 34 and the evaporator 30 by the pump 31 for organic fluid.

As such, the organic fluid path 9, together with the evaporator 30, the power turbine 32, the economizer 34 and the condenser 36, constitutes an organic Rankine cycle.

Next, operation | movement of the heat recovery generator of the said structure is demonstrated using FIG.

The jacket cooling water guided to the cylinder jacket 2 by the jacket cooling water pump 12 is heated up by cooling the cylinder block or the like in the cylinder jacket 2 and then led to the preheater 1. In the preheater 1, heat exchange is performed between the fruit water flowing through the heat recovery path 7 and the jacket cooling water, and the sensible heat of the jacket cooling water is recovered to the fruit water of the heat recovery path 7. The fruit water temperature after heat recovery from the jacket cooling water is, for example, 80 to 90 ° C.

The air compressed by the turbocharger of the diesel engine is cooled by the first air cooler 5. At this time, the fruit water of the heat recovery path 7 flowing in the first air cooler 5 is heated by the compressed air, thereby recovering heat from the compressed air. The fruit water temperature after heat recovery in the first air cooler 5 is, for example, 130 to 140 ° C.

The fruit water recovered from the preheater 1 and recovered from the first air cooler 5 to a high temperature is led to the evaporator 30, and the organic fluid circulated through the organic fluid path 9. Heat exchange. The organic fluid is heated in the evaporator 30 by sensible heat of the fruit water and evaporated to vaporization. The organic fluid which has evaporated and became high enthalpy is guided to the power turbine 32, and rotates the power turbine 32 by the thermal fall. The rotational output of the power turbine 32 is obtained, and electric power generation is performed in the generator 38.

The organic fluid (gas phase) completed in the power turbine 32 is led to the condenser 36 after preheating the organic fluid (liquid phase) before the evaporator 30 is introduced into the economizer 34, and is led to the condenser 36. It is condensed and liquefied by cooling with cooling water.

As mentioned above, according to this embodiment, the following effects are exhibited.

As the heat source of the organic Rankine cycle, it was assumed that the heat recovered by the jacket cooling water (engine cooling water) and the first air cooler 5 was used. As such, instead of using exhaust gas of a diesel engine having a high temperature level, for example, 250 ° C. or higher, a jacket cooling water (for example, 80 to 90 ° C.) that is not effectively used because the temperature level is lower than the exhaust gas, and A 1st air cooler (for example, 130-140 degreeC) can be used. In particular, since only the jacket cooling water is low as the temperature level of the heat source for driving the organic Rankine cycle, heat recovery is also performed from the first air cooler 5, thereby improving the realization of power generation by the organic Rankine cycle.

Moreover, the fruit water which flowed through the heat recovery path 7 recovers heat from the jacket cooling water, and further recovers heat from the first air cooler 5, and then evaporator 30 is to evaporate the organic fluid. In this way, since the fruit water heat-recovered from the jacket cooling water and the first air cooler 5 is directly guided to the evaporator 30 without intervening with other fruits, recovery heat can be induced to the evaporator 30 with little heat loss. Can be.

[Second Embodiment]

Next, 2nd Embodiment of this invention is described using FIG. This embodiment is shown in the state containing the electric power system about the structure at the time of applying the heat recovery power generation apparatus of 1st Embodiment to the heat recovery system of a ship. Therefore, about the structure similar to 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

As shown in FIG. 2, the jacket cooling water which cooled and heated the cylinder jacket 2 flows to the preheater 1, and heat-exchanges with the fruit water which circulates through the waste heat recovery system 7 by the waste heat collection pump 24. As shown in FIG. do. The fruit water collected and recovered by the preheater 1 is guided to the first air cooler 5, and is heated up by removing the heat of compression from the compressed air discharged from the supercharger 40 and then leading to the evaporator 30. The organic fluid heated and evaporated by the fruit water in the evaporator 30 drives the power turbine 32, whereby power generation is performed in the generator 38. The electric power generated in the generator 38 is guided to the in-vehicle system 44 after being frequency adjusted in the inverter device 42.

The exhaust gas of the diesel engine which is the propulsion period is guided to the exhaust gas economizer (exhaust gas heat exchanger) 46. The exhaust gas economizer 46 recovers the sensible heat of the exhaust gas, generates superheated steam in the superheater 48, and drives the steam turbine 50. The exhaust gas power turbine (gas turbine) 54 is connected to the steam turbine 50 via the clutch 52. The exhaust gas power turbine 54 is driven by exhaust gas guided from the exhaust manifold 56 of the diesel engine.

The rotational output obtained by these steam turbine 50 and the power turbine 54 is transmitted to the generator 60 via the speed reducer 58, and electric power generation is performed by this generator 60. The electric power generated by the generator 60 is output to the in-vehicle system 44.

A plurality of (three in FIG. 2) diesel engines for power generation and a generator 64 are connected in parallel to the inboard system 44. These diesel engines for power generation 62 are started and stopped in accordance with the demand power in the ship.

Moreover, the axial generator motor 66 is connected to the in-vessel system 44. The generator motor 66 is capable of adding power from the in-vehicle system 44 to add the ship propulsion propeller 68, and recovers and generates power from the ship propeller propeller 68, Power supply to the system 44 in a ship is made possible.

According to this embodiment, the following effect is exhibited.

In addition to the heat recovery power generation unit by organic Rankine cycle operating at 130 to 140 ° C., a steam turbine capable of high efficiency can be expected for exhaust gas of a marine propulsion diesel engine having a high temperature level such as 250 ° C. or higher. ) To develop it. This enables heat recovery and generation with high efficiency over a wide temperature range.

Moreover, since the power generation is further provided by the exhaust gas power turbine 54 driven by the exhaust gas, heat recovery recovery power generation can be realized with higher efficiency.

In the present embodiment, power generation is performed using both the steam turbine 50 and the exhaust gas power turbine 54. The present invention is not limited to this, but the steam turbine 50 alone or the exhaust gas power. It is also possible to use only the turbine 54.

[Third embodiment]

Next, 3rd Embodiment of this invention is described using FIG. In addition to the first embodiment and the second embodiment, the present embodiment differs from the foregoing embodiments in that the steam obtained in the exhaust gas economizer 46 is used as a heat source of the organic Rankine cycle. Therefore, about the structure similar to 1st Embodiment and 2nd Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

The exhaust gas economizer 46 is formed with an evaporator 49 located at a lower temperature side (exhaust gas flow downstream) than the superheater 48. The vapor evaporated in the evaporator 49 is directed to the steam drum 72. Steam remaining above the steam drum 72 is led to a heater (fourth heat recovery device) 70. In the heater 70, the fruit water flowing through the heat recovery system 7 is heated, and is led to the evaporator 30.

Thus, in this embodiment, since the fruit water heated by the 1st air cooler 5 is heated further by the heater 70, the heating temperature of the organic refrigerant in the evaporator 30 can be raised. Thereby, power generation by an organic Rankine cycle can be made highly efficient. In addition, since the vapor obtained from the exhaust gas economizer 46 can be used effectively, heat recovery power generation can be made more efficient.

3, the code | symbol 3 has shown the ship propulsion diesel engine, and the cylinder jacket 2 is shown typically at the side. Further, reference numeral 74 denotes a steam turbine condenser connected to the downstream side of the steam turbine 50, reference numeral 76 denotes a plurality of pumps, reference numeral 78 denotes a ground condenser, reference numeral 80 denotes an atmospheric pressure condenser, and reference numeral 82 denotes a feed water pump. Reference numeral 84 denotes a boiler drum water circulation pump for sending water in the steam drum 72 to the evaporator 49, and reference numeral 86 denotes a steam drum level control valve for adjusting the water level in the steam drum 72.

[Fourth Embodiment]

Next, 4th Embodiment of this invention is described using FIG. This embodiment differs in the configuration of the heat recovery path 7 'from the first embodiment. Therefore, about the structure similar to 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

As shown in FIG. 4, in this embodiment, the jacket cooling water is used as it is as the fruit water of the heat recovery path 7 ′. That is, the jacket cooling water flowing out from the cylinder jacket 2 flows to the first air cooler (third heat recovery device) 5. The jacket cooling water cooled by raising the compressed air in the first air cooler 5 and raising the temperature is returned to the jacket cooling water pump 12 after evaporating the organic fluid in the evaporator 30.

Thus, according to this embodiment, since the jacket cooling water is used as a heat medium for heat recovery, the preheater 1 (refer FIG. 1) which heat-exchanges with jacket cooling water can be omitted, and a simplified structure can be implement | achieved. . Moreover, since the jacket cooling water heat-recovered from the 1st air cooler 5 is guide | induced directly to the evaporator 30 without interposing another fruit, recovery heat can be guide | induced to the evaporator 30 with little heat loss.

[Fifth Embodiment]

Next, 5th Embodiment of this invention is described using FIG. The present embodiment differs from the first embodiment in that the fruit circulation path 8 is formed between the heat recovery path 7 and the organic fluid path 9. Therefore, about the structure similar to 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

As shown in FIG. 5, the fruit circulation path 8 is formed between the heat recovery path 7 and the organic fluid path 9. This fruit circulation path 8 is a closed circuit, and the fruit circulation pump 11 for circulating a heat medium is formed. The fruit is circulated through the heat recovery heat exchanger 13 and the evaporator 30 by the fruit circulation pump 11. In the heat recovery heat exchanger (13), heat exchange is performed to recover heat from the fruit water of the heat recovery path (7).

As the fruit flowing through the fruit circulation path 8, for example, a heat medium oil having a boiling point higher than that of the fruit recovery path 7 is used. As heat medium oil, Valle Island (registered trademark) available from Matsumura Petroleum Co., Ltd. is used, for example.

In this manner, instead of guiding the fruit water of the heat medium path 7 to the evaporator 30 as in the first embodiment, the arrangement recovered through the fruit circulation path 8 may be guided to the evaporator 30. .

Since water is used in the heat recovery path 7, it is necessary to pressurize the inside of the heat recovery path 7 so that the water does not boil and become vapor, and depending on the inlet air temperature of the first air cooler 5, It becomes specification. Thus, when the fruit circulation path 8 is formed as in the present embodiment, and mainly fruit oil having a higher boiling point than water is used, the pressure of the fruit circulation path 8 can be used at atmospheric pressure, and the heat recovery recovery path 7 Can be configured as a low pressure line separated from

In addition, in the case where there is an arrangement constraint in which the organic Rankine cycle power generator 10 cannot be installed near the diesel engine having the heat recovery path 7, the heat recovery path 8 is introduced. After avoiding the distance of the line of (7), it becomes possible to induce an arrangement in the power generation apparatus 10 for organic Rankine cycles using the low pressure line of the fruit circulation path 8.

[Sixth Embodiment]

Next, 6th Embodiment of this invention is described using FIG. In the present embodiment, the same fruit circulation path 8 (see FIG. 5) as in the fifth embodiment is formed between the heat recovery path 7 ′ and the organic fluid path 9 in the fourth embodiment. The points are different. Therefore, about the structure similar to 4th Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

As shown in FIG. 6, the fruit circulation path 8 is formed between the heat recovery path 7 ′ and the organic fluid path 9. This fruit circulation path 8 is a closed circuit, and the fruit circulation pump 11 for circulating a heat medium is formed. The fruit is circulated through the heat recovery heat exchanger 13 and the evaporator 30 by this fruit circulation pump 11. In the heat recovery 13, heat exchange is performed so as to recover heat from the jacket cooling water in the heat recovery path 7 ′.

As the fruit flowing through the fruit circulation path 8, for example, a heat medium oil having a boiling point higher than that of the fruit recovery path 7 is used. As heat medium oil, Valle Island (registered trademark) available from Matsumura Petroleum Co., Ltd. is used, for example.

As described above, the jacket cooling water of the heat medium path 7 'is not led to the evaporator 30 as in the fourth embodiment, but the arrangement recovered through the fruit circulation path 8 is guided to the evaporator 30. do.

Similarly to the fifth embodiment, the present embodiment also introduces the fruit circulation path 8, thereby avoiding the line of the heat recovery path 7 from being far, and then using the low pressure line of the fruit circulation path 8. The configuration becomes possible.

In addition, although the heat recovery power generation apparatus of each embodiment mentioned above was demonstrated using the application to the ship as an example, this invention is not limited to this, For example, it can also be applied to the internal combustion engine for land used for power generation etc. .

1: preheater (first array recoverer)
5: 1st air cooler (2nd array recoverer, 3rd array recoverer)
7, 7 ': array recovery path
8: fruit circulation path
9: organic fluid pathway
10: heat recovery generator
30: evaporator
31: pump for organic fluid
32: power turbine (turbine)
36 condenser
38: generator
70: heater (fourth array recovery unit)

Claims (9)

An array recovery path for heat recovery in an engine coolant for cooling the internal combustion engine body and an air cooler for cooling the compressed air discharged from the supercharger of the internal combustion engine;
An evaporator for evaporating the organic fluid by the recovered heat recovered in the heat recovery path,
A turbine driven by the organic fluid evaporated by the evaporator;
A generator generated by the rotational output of the turbine,
And a condenser for condensing the organic fluid that has passed through the turbine. The method of claim 1,
The array recovery path,
A first heat recovery unit performing heat exchange with the engine cooling water;
And a second heat recovery unit as the air cooler,
And a heat recovery medium heat-recovered by the first heat recovery device and the second heat recovery device heat exchange with the organic fluid in the evaporator. The method of claim 1,
The heat recovery path uses the engine cooling water as a heat recovery medium,
And a third heat recovery device as the air cooler for performing heat exchange between the engine coolant and the compressed air.
And the engine cooling water heat-recovered by the third heat recovery device exchanges heat with the organic fluid in the evaporator. The method of claim 1,
While the fruit is circulated, the fruit has a fruit circulation path in which the fruit heat exchanges with the organic fluid,
The array recovery path,
A first heat recovery unit performing heat exchange with the engine cooling water;
A second heat recovery unit as the air cooler,
And a heat recovery medium heat-recovered by the first heat recovery device and the second heat recovery device. The method of claim 1,
While the fruit is circulated, the fruit has a fruit circulation path in which the fruit heat exchanges with the organic fluid,
The heat recovery path uses the engine cooling water as a heat recovery medium,
And a third heat recovery device as the air cooler for performing heat exchange between the engine coolant and the compressed air.
And the engine cooling water heat-recovered by the third heat recovery unit exchanges heat with the fruit of the fruit circulation path. 6. The method according to any one of claims 1 to 5,
And a steam turbine generator driven by steam generated in an exhaust gas heat exchanger which exchanges heat with the exhaust gas of the internal combustion engine. The method according to claim 6,
The exhaust gas heat exchanger includes an evaporator for evaporating water and a superheater for overheating steam generated by the evaporator.
The heat recovery recovery device is provided with a fourth heat recovery device that exchanges heat with steam obtained by the evaporator. The method according to any one of claims 1 to 7,
A heat recovery power generation device including a gas turbine generator driven by exhaust gas of the internal combustion engine. The ship provided with the heat recovery power generation apparatus in any one of Claims 1-8.

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