JP2015017771A - Boiler system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a system that has a simple structure for storing waste heat of a prime mover and using the stored waste heat.SOLUTION: A boiler system 1 is provided with: a boiler part 50 for heating boiler water by using waste heat of a prime mover 3 as a heat source; a second pump 55 for circulating the boiler water via a second circulation passage 522; and a heat storage part 59 for exchanging heat between a heat storage material and the boiler water flowing through the second circulation passage 522. In the heat storage part 59, the heat storage material is heated by the boiler water to store heat when the temperature of the heat storage material is lower than the temperature of the boiler water, and the boiler water is heated by the heat storage material when the temperature of the heat storage material is higher than the temperature of the boiler water. In this way, by adding the heat storage part 59, the second pump 55, and the second circulation passage 522 to the boiler part 50 for supplying steam to a steam system in a ship, the boiler system 1 that has a simple structure for storing the waste heat of the prime mover 3 and heating the boiler water by using the stored waste heat can be provided.

Description

  The present invention relates to a boiler system.

  Conventionally, in a large vessel, an exhaust gas economizer that generates steam by heating boiler water with waste heat of exhaust gas discharged from a main engine is provided in a chimney. For example, in the exhaust gas economizer system disclosed in Patent Document 1, boiler water stored in an auxiliary boiler is sent to an exhaust gas economizer by a boiler water circulation pump, heated by the exhaust gas economizer, and then returned to the auxiliary boiler.

  In patent document 2, the energy storage system which stores energy in a ship is proposed. In the energy storage system, a waste heat recovery device that recovers waste heat of exhaust from the main engine with a heat transfer oil is provided, and the heat transfer oil heated in the waste heat recovery device is used as a heat storage material heat exchange device and a steam generator. Supplied to the device. In the heat storage material heat exchange device, the heat storage material such as molten salt is heated by the heat medium oil to perform heat storage. In the steam generator, water is evaporated by the heat transfer oil to drive the steam turbine, and power is generated by a generator connected to the steam turbine. Part of the steam supplied to the steam turbine is taken out from the middle stage of the steam turbine and used as process steam in the ship. During berthing where the waste heat from the exhaust from the main engine cannot be used, the steam in the steam generator is heated by the heat of the heat storage material to generate steam, and power is generated by the steam.

  In patent document 3, the thermal storage system for ships is proposed. In the heat storage system, water is heated by an exhaust gas economizer to generate steam, and the steam is supplied to the heat exchange means, whereby the heat storage medium sent from the heat storage tank to the heat exchange means is heated to store the heat. Heat is stored in the tank. In the heat storage use operation mode, the use side heat medium is sent from the use device to the heat exchange means, and the use side heat medium is heated by the heat storage medium supplied from the heat storage tank to the heat exchange means.

  On the other hand, Patent Document 4 discloses a power generation device that generates power using exhaust gas from a diesel generator. In the power generation device, the organic fluid circulating in the circulation path is heated via a heat exchanger by water or steam heated by exhaust gas from a diesel generator or the like, and the turbine is driven by the organic fluid to generate power by the generator. Is done. That is, the power generation apparatus is a waste heat recovery apparatus that performs an organic rankine cycle (ORC) using an organic medium as a working fluid.

JP2011-196646A JP 2010-116847 A JP 2011-75227 A Registered Utility Model No. 3044386

  By the way, in the marine energy storage system of patent document 2, since the stored thermal energy is used as a power source for power generation, a large-scale heat storage facility is required. Moreover, since the conversion efficiency at the time of converting heat energy into motive power is low, it is difficult to efficiently use the stored heat energy. On the other hand, in the marine heat storage system of Patent Document 3, a system that recovers waste heat of the main engine, a system that stores heat in the heat storage tank and releases heat from the heat storage tank, and a heat medium that uses the heat energy of the heat storage tank Since the system which supplies to a utilization apparatus via a device is needed separately, the structure of the thermal storage system for ships will be complicated.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a system having a simple structure that stores waste heat of a prime mover and uses the stored waste heat.

  The invention according to claim 1 is a boiler system that stores a liquid medium, heats the medium using waste heat from a prime mover as a heat source, and sends the liquid medium from the boiler section for circulation. From a medium having a pump that circulates to the boiler section through a passage and a heat storage material, exchanging heat between the heat storage material and a medium flowing through the circulation path, and the heat storage material flowing through the circulation path A heat storage unit that stores heat with the heat storage material when the temperature is low, and heats the medium with the heat storage material when the heat storage material is hotter than the medium flowing through the circulation path.

  Invention of Claim 2 is the boiler system of Claim 1, Comprising: The said boiler part sends out a liquid medium from the boiler main body which stores a liquid medium, and the said boiler main body, and other circulation Another pump that circulates to the boiler main body via a passage, and an exhaust heat exchanger that heats the medium flowing through the other circulation passage using the exhaust gas flowing through the exhaust passage of the prime mover as a heat source.

  Invention of Claim 3 is a boiler system of Claim 1, Comprising: The said boiler part is equipped with the boiler main body through which the said exhaust path penetrates while storing a liquid medium, Exhaust gas which flows through the said exhaust path As a result, the medium in the boiler body is heated.

  Invention of Claim 4 is a boiler system in any one of Claim 1 thru | or 3, Comprising: It arrange | positions on the piping which guides a medium from the said thermal storage part to the said boiler part in the said circulation path, The said prime mover The apparatus further includes a compressed air heat exchanger that heats the medium using compressed air that is pressurized intake air supplied to the heat source as a heat source.

  Invention of Claim 5 is a boiler system in any one of Claim 1 thru | or 4, Comprising: The temperature difference which subtracted the temperature of the said thermal storage material in the said thermal storage part from the temperature of the medium in the said boiler part is calculated | required. A temperature difference acquisition unit; and a flow rate control unit that controls a flow rate of a medium guided from the heat storage unit to the boiler unit based on the temperature difference, and as the temperature difference increases, the flow rate control unit The flow rate decreases.

  Invention of Claim 6 is a boiler system in any one of Claim 1 thru | or 5, Comprising: It arrange | positions on the piping which guides a medium from the said thermal storage part to the said boiler part in the said circulation path, The said thermal storage A recovery device that recovers energy from the medium sent from the section, wherein the recovery device heats and vaporizes the working fluid that is an organic medium using the medium flowing through the circulation path as a heat source; and An expander that expands the working fluid vaporized in the ORC heat exchanger to recover mechanical energy, a condenser that condenses and liquefies the working fluid expanded in the expander, and the condenser An ORC pump for delivering the liquefied working fluid to the ORC heat exchanger.

  The invention according to claim 7 is the boiler system according to any one of claims 1 to 6, wherein the medium is boiler water, and steam of the boiler water is generated in the boiler section.

  Invention of Claim 8 is a boiler system of Claim 7, Comprising: The steam compression part which compresses the vapor | steam of the boiler water sent to the exterior from the said boiler part is further provided.

  A ninth aspect of the present invention is the boiler system according to any of the first to eighth aspects, wherein the prime mover is a main engine of a ship, and the boiler unit is an auxiliary boiler of the ship.

  In the present invention, it is possible to provide a system having a simple structure that stores the waste heat of the prime mover and uses the stored waste heat.

It is a figure which shows the structure of the boiler system which concerns on the 1st Embodiment of this invention. It is a figure which shows an example of the flow control of boiler water. It is a figure which shows the structure of a boiler system. It is a figure which shows the structure of the boiler system which concerns on the 2nd Embodiment of this invention. It is a figure which shows the structure of a boiler system. It is a figure which shows the structure of the boiler system which concerns on the 3rd Embodiment of this invention. It is a figure which shows the structure of a boiler system. It is a figure which shows the structure of the boiler system which concerns on the 4th Embodiment of this invention. It is a figure which shows the structure of a boiler system.

  FIG. 1 is a diagram showing a configuration of a boiler system 1 according to a first embodiment of the present invention. The boiler system 1 is used, for example, as an auxiliary boiler system for a relatively large ship. In FIG. 1, the motor | power_engine 2 with a supercharger utilized as a main engine of a ship is also shown. In the boiler system 1, boiler water as a medium is heated using waste heat of the motor 2 with a supercharger. Steam generated from the heated boiler water is used as a heating source for fuel oil, lubricating oil, domestic water, etc. in the ship.

  The supercharger-equipped prime mover 2 includes a marine prime mover 3 that is an internal combustion engine (hereinafter simply referred to as “prime mover 3”) and a turbocharger 4 that is a turbocharger. The prime mover 3 is a main engine of a ship, for example, a two-cycle diesel engine. The supercharger 4 includes a turbine 41 and a compressor 42 that is mechanically connected to the turbine 41. The prime mover 3 and the supercharger 4 are connected by a scavenging path 31 and an exhaust path 32. The exhaust path 32 guides the exhaust from the prime mover 3 to the turbine 41.

  The turbine 41 is rotated by the exhaust gas supplied from the prime mover 3 through the exhaust passage 32. The exhaust used for the rotation of the turbine 41 is discharged to the outside of the supercharger-equipped prime mover 2 through the exhaust passage 32. The compressor 42 is guided to the supercharger 4 through the intake passage 43 from the outside of the supercharger-equipped prime mover 2 using the rotational force generated in the turbine 41 (that is, using the rotation of the turbine 41 as power). Pressurize and compress the intake air (air). Compressed air (hereinafter referred to as “scavenging”) pressurized by the compressor 42 is cooled by a compressed air heat exchanger 56 (described later) provided on the scavenging passage 31, and then is supplied to the prime mover 3. Supplied. Thus, in the supercharger 4, the intake air is pressurized using the exhaust gas, and scavenging is generated. The scavenging passage 31 is a passage that guides pressurized intake air from the supercharger 4 to the prime mover 3, that is, a pressurized intake passage. The boiler system 1 may be provided with a scavenging cooler that is disposed on the downstream side of the compressed air heat exchanger 56 in the scavenging passage 31 and further cools the scavenged air sent from the compressed air heat exchanger 56. (The same applies to other embodiments).

  The boiler system 1 includes a boiler device 5. The boiler device 5 includes a boiler unit 50, a pump 55, a heat storage unit 59, a switching unit 572, a compressed air heat exchanger 56, a flow rate control unit 571, a first measurement unit 581, and a second measurement unit 582. With. In FIG. 1, “heat storage mode” in which heat storage by the heat storage unit 59 is performed will be described. The boiler unit 50 includes a boiler body 51, another pump 53, and an exhaust heat exchanger 54. In the following description, the pumps 53 and 55 are referred to as “first pump 53” and “second pump 55”, respectively.

  The boiler body 51 is disposed at a position away from the chimney (so-called funnel) of the ship and stores a liquid medium (that is, liquid boiler water). The boiler main body 51 is provided with the first measurement unit 581 described above. The temperature of the boiler water in the boiler body 51 is measured by the first measuring unit 581. The boiler body 51 is also provided with a burner and a water supply unit (not shown). The burner heats boiler water in the boiler body 51 as necessary. The said water supply part supplies boiler water in the boiler main body 51 as needed, such as when the boiler water in the boiler main body 51 reduces.

  The boiler body 51, the second pump 55, the heat storage unit 59, the switching unit 572, the compressed air heat exchanger 56, and the flow rate control unit 571 are connected in this order by a circulation path 522 through which boiler water circulates. In the boiler part 50, the boiler main body 51, the 1st pump 53, and the exhaust heat exchanger 54 are connected in the said order by the other circulation path 521 through which boiler water circulates. In the following description, the circulation paths 521 and 522 are referred to as “first circulation path 521” and “second circulation path 522”, respectively. The first circulation path 521 and the second circulation path 522 form a common flow path between the boiler body 51 and the branching part 52a, and branch off at the branching part 52a. Note that the first circulation path 521 and the second circulation path 522 may be individually connected to the boiler body 51.

  In the boiler unit 50, liquid boiler water is sent from the boiler body 51 to the first circulation path 521 by driving the first pump 53. The boiler water sent out from the boiler body 51 passes through the first pump 53 via the first circulation path 521 and further passes through the exhaust heat exchanger 54, as indicated by arrows in FIG. Circulates to the boiler body 51.

  The exhaust heat exchanger 54 is disposed in the chimney of the ship, and is disposed on the downstream side of the turbine 41 on the exhaust path 32 of the supercharger-equipped prime mover 2. In the exhaust heat exchanger 54, the liquid boiler water flowing through the first circulation path 521 is heated using the exhaust from the turbine 41 flowing through the exhaust path 32 (that is, the exhaust from the prime mover 3 after passing through the turbine 41) as a heat source. Is done. In other words, in the exhaust heat exchanger 54, boiler water is heated using the waste heat of the supercharger-equipped prime mover 2 included in the exhaust as a heat source. The temperature of the exhaust gas passing through the exhaust heat exchanger 54 varies depending on the output of the prime mover 3, the ambient temperature, and the like. The exhaust temperature when the output of the prime mover 3 is the maximum output (100% output) is, for example, about 230 ° C. In the exhaust heat exchanger 54, a part of the boiler water flowing into the exhaust heat exchanger 54 is vaporized (evaporated). A mixed fluid of gaseous boiler water and liquid boiler water is sent from the exhaust heat exchanger 54 to the boiler body 51.

  That is, the boiler unit 50 is an apparatus (so-called exhaust gas economizer) that stores liquid boiler water and heats the boiler water using the exhaust gas flowing through the exhaust passage 32 of the prime mover 3 as a heat source to generate steam of the boiler water. Used as an auxiliary boiler for ships. The temperature and pressure of the boiler water in the boiler body 51 are, for example, about 135 ° C. and about 0.25 MPa (megapascal) to about 165 ° C. and about 0.6 MPa. Steam of boiler water in the boiler body 51 is supplied to a steam system (not shown) in the ship via a steam pipe 524 connected to the upper part of the boiler body 51.

  In the boiler system 1, a branch pipe 526 that branches from the steam pipe 524 and joins to the steam pipe 524 is provided between the boiler body 51 and the steam system. On branch pipe 526, a steam compression section (hereinafter simply referred to as “compression section 511”) for compressing steam of boiler water sent from boiler section 50 to an external steam system is provided. Valves are provided on the steam pipe 524 and the branch pipe 526. By switching these valves, the supply path of the steam supplied from the boiler body 51 to the steam system in the ship is switched between a path that passes through the compression section 511 and a path that does not pass through the compression section 511. In the heat storage mode, the compression unit 511 is not used, and the steam sent from the boiler body 51 is supplied to the steam system in the ship without passing through the compression unit 511.

  In the boiler device 5, liquid boiler water is sent from the boiler body 51 to the second circulation path 522 by driving the second pump 55. The boiler water sent out from the boiler body 51 is connected to the second pump 55, the heat storage unit 59, the switching unit 572, and the compressed air heat exchanger 56 via the second circulation path 522 as shown by arrows in FIG. And flow through the flow rate control unit 571 in this order and circulate to the boiler body 51.

  The heat storage part 59 has a heat storage material. In the heat storage unit 59, heat exchange is performed between the heat storage material and boiler water flowing through the second circulation path 522. For example, when the output of the prime mover 3 is equal to or higher than the service output (CSO: Continuous Service Output), the temperature of the boiler water sent from the boiler body 51 is relatively high, and therefore the temperature of the heat storage material is It is lower than the temperature of the boiler water flowing through the two circulation paths 522. Thus, when the heat storage material is at a lower temperature than the boiler water flowing through the second circulation path 522 in the heat storage unit 59, the heat storage material is heated by the boiler water, and heat storage is performed in the heat storage unit 59. The temperature of the heat storage material in the heat storage unit 59 is measured by the second measurement unit 582.

  In the heat storage unit 59, the boiler water is cooled by the heat storage material. The boiler water sent from the heat storage unit 59 is guided to the switching unit 572. The switching unit 572 is a three-way valve provided on the second circulation path 522, for example. The boiler water that has passed through the switching unit 572 is guided to the compressed air heat exchanger 56 by the second circulation path 522. In the switching unit 572, a branch pipe 525 indicated by a broken line in FIG. 1 branches from the second circulation path 522, and the second circulation path is formed at the junction 52c between the compressed air heat exchanger 56 and the flow rate control unit 571. Merge to 522. In the heat storage mode, the branch pipe 525 is not used. The “heat supply mode” using the branch pipe 525 will be described later. The temperature of boiler water heading from the switching unit 572 to the compressed air heat exchanger 56 is, for example, about 100 to 130 ° C.

  The compressed air heat exchanger 56 is arranged on a pipe that guides boiler water from the heat storage unit 59 to the boiler body 51 of the boiler unit 50 on the second circulation path 522. Specifically, the compressed air heat exchanger 56 is disposed between the heat storage unit 59 and the flow rate control unit 571 on the second circulation path 522. The compressed air heat exchanger 56 is also disposed on the scavenging path 31 between the compressor 42 and the prime mover 3. In the compressed air heat exchanger 56, the liquid boiler water flowing through the second circulation path 522 is heated using the scavenging in the scavenging path 31 supplied from the compressor 42 to the prime mover 3 as a heat source. In other words, in the compressed air heat exchanger 56, the boiler water is heated using the waste heat of the prime mover-equipped motor 2 included in the scavenging as a heat source.

  From the compressed air heat exchanger 56, liquid boiler water or a mixed fluid of gaseous boiler water and liquid boiler water is sent out. The boiler water heated in the compressed air heat exchanger 56 passes through the flow rate control unit 571 and is returned to the boiler body 51. The temperature of the scavenging air passing through the compressed air heat exchanger 56 varies depending on the output of the prime mover 3, the ambient temperature, and the like. The scavenging temperature when the output of the prime mover 3 is the maximum output (100% output) is, for example, about 220 ° C. When the output of the prime mover 3 decreases, the scavenging temperature also decreases. The temperature of boiler water sent from the compressed air heat exchanger 56 varies depending on the temperature of boiler water flowing into the compressed air heat exchanger 56, the temperature of scavenging air passing through the compressed air heat exchanger 56, and the like. The temperature of the boiler water heading from the compressed air heat exchanger 56 to the flow rate control unit 571 is, for example, about 135 to 165 ° C.

  The flow rate control unit 571 is, for example, a three-way valve provided on the second circulation path 522. In the flow rate control unit 571, a branch pipe 523 indicated by a broken line in FIG. 1 branches from the second circulation path 522, and in the junction 52 b between the boiler body 51 and the second pump 55, the second circulation path 522 is connected. Join.

  In the boiler device 5, as described above, the temperature of the boiler water in the boiler body 51 is measured by the first measurement unit 581, and the temperature of the heat storage material of the heat storage unit 59 is measured by the second measurement unit 582. The measurement values of the first measurement unit 581 and the second measurement unit 582 are sent to the temperature difference acquisition unit 573 connected to the flow rate control unit 571. In the temperature difference acquisition unit 573, the temperature of the heat storage material in the heat storage unit 59 is subtracted from the temperature of the boiler water in the boiler body 51 of the boiler unit 50 based on the measurement values from the first measurement unit 581 and the second measurement unit 582. Temperature difference. And based on the said temperature difference, the flow volume of the boiler water guide | induced to the boiler main body 51 of the boiler part 50 through the compressed air heat exchanger 56 from the heat storage part 59 is controlled by the flow volume control part 571.

  FIG. 2 is a diagram showing an example of boiler water flow control by the flow control unit 571. The horizontal axis in FIG. 2 indicates the temperature difference Δt between the boiler water and the heat storage material obtained by the temperature difference acquisition unit 573. The vertical axis in FIG. 2 indicates the proportion of boiler water that is returned from the compressed air heat exchanger 56 to the flow rate control unit 571 and returned to the boiler body 51 through the flow rate control unit 571 (hereinafter, “ "Reflux ratio"). In other words, the recirculation ratio is determined from the heat storage unit 59 to the compressed air heat exchanger 56 and the flow rate control unit 571 with respect to the flow rate of boiler water guided from the heat storage unit 59 via the compressed air heat exchanger 56 to the flow rate control unit 571. It is the ratio of the flow volume of the boiler water guide | induced to the boiler main body 51 via.

  When the reflux ratio is 100%, the entire amount of boiler water led from the compressed air heat exchanger 56 to the flow rate control unit 571 is returned to the boiler body 51 through the flow rate control unit 571. On the other hand, when the recirculation ratio is less than 100%, the boiler water having a flow rate obtained by multiplying the flow rate of the boiler water sent from the compressed air heat exchanger 56 by the ratio corresponding to the value on the vertical axis passes through the flow rate control unit 571. Is returned to the boiler body 51. Further, the remaining boiler water is guided to the branch pipe 523 by the flow rate control unit 571, merged with the boiler water sent from the boiler body 51 at the junction unit 52 b, and then the second boiler channel 522 through the second circulation path 522. 2 is guided to the pump 55.

  In the example shown in FIG. 2, when the temperature difference Δt is 0 or more and t1 or less, the reflux ratio is 100%, and the entire amount of boiler water from the compressed air heat exchanger 56 is returned to the boiler body 51. Thereby, the waste heat of the scavenging gas collected in the compressed air heat exchanger 56 can be efficiently used for heating (or maintaining the temperature) of the boiler water in the boiler body 51.

  On the other hand, when the temperature difference Δt is larger than t1, the reflux rate is less than 100%, a part of the boiler water from the compressed air heat exchanger 56 is returned to the boiler body 51, and the remaining boiler water is used as the boiler water. It returns to the second pump 55 via the branch pipe 523 without passing through the main body 51. When the temperature difference Δt is greater than t1 and equal to or less than t2, the reflux ratio gradually decreases as controlled by the flow rate control unit 571 as the temperature difference Δt increases. In other words, as the temperature difference Δt increases, the flow rate of the boiler water led from the heat storage unit 59 to the boiler body 51 is gradually reduced by the control by the flow rate control unit 571. When the temperature difference Δt is t2 or more, the reflux ratio is constant at a predetermined ratio that is greater than 0% and less than 100%.

  As described above, in the heat storage unit 59, the temperature of the boiler water decreases when the heat storage material is heated by the boiler water. When the temperature difference Δt obtained by subtracting the temperature of the heat storage material from the temperature of the boiler water increases, the temperature drop of the boiler water in the heat storage unit 59 also increases. Therefore, when the temperature difference Δt is large, if the total amount of boiler water whose temperature has been reduced in the heat storage unit 59 is returned to the boiler body 51, the temperature of the boiler water in the boiler body 51 falls below a predetermined temperature range. In addition, the steam supply from the boiler body 51 to the ship may be adversely affected.

  Therefore, in the boiler system 1 shown in FIG. 1, when the temperature difference Δt is large, the temperature of the boiler water in the boiler body 51 is reduced by reducing the flow rate of the boiler water returning from the heat storage unit 59 to the boiler body 51. It is possible to suppress or prevent the temperature from becoming lower than the predetermined temperature. As a result, it is possible to supply boiler water steam at a desired temperature to the steam system in the ship. Further, as the temperature difference Δt increases, the temperature of the boiler water in the boiler body 51 becomes lower than a predetermined temperature by gradually decreasing the flow rate of the boiler water returning from the heat storage unit 59 to the boiler body 51. Further suppression or prevention can be achieved. That is, the flow rate control unit 571 is a temperature control unit that controls the temperature of boiler water in the boiler body 51 of the boiler unit 50.

  Moreover, in the boiler system 1, the temperature of the boiler water of parts other than the boiler main body 51 in the boiler part 50 is measured by the 1st measurement part 581, and based on the temperature difference which subtracted the temperature of the thermal storage material from the temperature of the said boiler water. Similarly to the above, the flow rate control of the boiler water by the flow rate control unit 571 may be performed. Even in this case, it is possible to suppress or prevent the boiler water temperature in the boiler body 51 from becoming lower than a predetermined temperature.

  FIG. 3 is a diagram showing the configuration of the boiler system 1 as in FIG. 1. However, in FIG. 3, illustration of the temperature difference acquisition part 573 is abbreviate | omitted (same also in FIG. 4 thru | or FIG. 9). Below, the heat supply mode in which the heat supply from the heat storage part 59 to the boiler part 50 is performed is demonstrated, referring FIG. The heat supply mode is performed, for example, when steam is supplied from the boiler system 1 to the ship while the prime mover 3 is stopped. When the prime mover 3 is stopped, the boiler water cannot be heated by exhaust in the exhaust heat exchanger 54, so the first pump 53 is stopped and the boiler water circulation in the first circulation path 521 is stopped. In FIG. 3, the first circulation path 521 is indicated by a broken line.

  When the boiler water heating by the exhaust is stopped, the temperature of the boiler water in the boiler body 51 is lowered. Therefore, the temperature of the boiler water that is sent from the boiler body 51 by the second pump 55 and flows through the second circulation path 522 is also lowered. The boiler water having a relatively low temperature passes through the second pump 55 and is guided to the heat storage unit 59, and heat exchange is performed between the boiler water and the heat storage material of the heat storage unit 59. The heat storage material is hotter than the boiler water flowing through the second circulation path 522 due to the thermal energy stored in the above-described heat storage mode. For this reason, in the heat storage unit 59, the boiler water is heated by the heat storage material, and a part of the boiler water flowing into the heat storage unit 59 is vaporized. Then, a mixed fluid of gaseous boiler water and liquid boiler water is sent from the heat storage unit 59 to the switching unit 572.

  In the heat supply mode, the flow path is switched by the switching unit 572, whereby the total amount of boiler water flowing from the heat storage unit 59 to the switching unit 572 is guided to the branch pipe 525. The boiler water guided to the branch pipe 525 passes through the merging portion 52 c, is guided to the flow rate control unit 571 by the second circulation path 522, and the entire amount is returned to the boiler body 51. Thus, in the heat supply mode, the boiler water sent from the boiler body 51 is heated by the heat energy stored in the heat storage material in the heat storage section 59 and returned to the boiler body 51. In other words, the thermal energy stored in the heat storage unit 59 is supplied to the boiler unit 50. In the heat supply mode, boiler water does not flow in the second circulation path 522 from the switching unit 572 through the compressed air heat exchanger 56 to the merging unit 52c. Is indicated by a broken line (the same applies to FIGS. 5, 7 and 9).

  Even in the heat supply mode, the steam in the boiler body 51 is supplied to the steam system in the ship via the steam pipe 524. In the heat supply mode, when the steam pressure of the boiler water delivered from the boiler body 51 is lower than a desired pressure, the valves on the steam pipe 524 and the branch pipe 526 are switched, and the boiler water from the boiler body 51 is switched. Are introduced into the compression section 511. The compressing unit 511 compresses the boiler water steam to a desired pressure, and then supplies the steam to the steam system.

  As described above, in the boiler system 1 shown in FIG. 1, the boiler unit 50 that stores liquid boiler water and heats the boiler water using the waste heat contained in the exhaust gas of the prime mover 3 as a heat source, and the boiler unit 50 Heat storage that exchanges heat between the second pump 55 that sends liquid boiler water and circulates it to the boiler section 50 via the second circulation path 522, and the heat storage material and the boiler water that flows through the second circulation path 522. A portion 59 is provided. And in the thermal storage part 59, when a thermal storage material is low temperature rather than the boiler water which flows through the 2nd circulation path 522, a thermal storage material is heated with boiler water, and thermal storage with a thermal storage material is performed, and a thermal storage material is the 2nd circulation path. When the temperature is higher than the boiler water flowing through 522, the boiler water is heated by the heat storage material.

  In this way, by adding the above-described heat storage unit 59, the second pump 55, and the second circulation path 522 to the boiler unit 50 that supplies steam to the steam system in the ship, the waste heat of the prime mover 3 can be stored and stored. A boiler system 1 having a simple structure that heats boiler water using the generated waste heat can be provided. Such a configuration of the boiler system 1 is particularly suitable for an auxiliary boiler system of a ship that requires a reduction in fuel consumption and has a limited space for arranging the apparatus.

  In the boiler system 1, the second circulation path 522 is arranged on a pipe for leading boiler water from the heat storage unit 59 to the boiler unit 50, and in the heat storage mode shown in FIG. 1, the scavenging gas supplied to the prime mover 3 is used as a heat source. A compressed air heat exchanger 56 for heating the water is provided. Thereby, the waste heat of the scavenging gas supplied to the prime mover 3 can be used for heating the boiler water in the heat storage mode. That is, in the boiler system 1, in the heat storage mode, the boiler water can be efficiently heated with a simple structure using a plurality of types of waste heat related to the prime mover 3, and the steam of the boiler water is efficiently generated. Can do. In addition, after the boiler water is cooled by the heat storage material in the heat storage unit 59 and heated by scavenging in the compressed air heat exchanger 56, the waste heat of the scavenging can be efficiently recovered in the boiler water.

  As described above, the boiler unit 50 sends the boiler water 51 from the boiler main body 51 disposed at a position away from the chimney of the ship and the boiler main body 51 to the boiler main body 51 via the first circulation path 521. And a first pump 53 that circulates, and an exhaust heat exchanger 54 that heats boiler water that is disposed on the exhaust path 32 and flows through the first circulation path 521 in the heat storage mode. Thereby, the structure (namely, structure provided in a chimney) provided on the exhaust path 32 among the boiler systems 1 can be reduced in size and simplified.

  In the boiler system 1, the compression part 511 which compresses the steam of the boiler water sent out from the boiler part 50 outside is provided. Thereby, in the heat supply mode, it is possible to prevent insufficient steam pressure of boiler water supplied to the steam system in the ship. Moreover, the steam pressure of the boiler water in the boiler body 51 can be lowered while supplying steam of boiler water having a desired pressure to the steam system. Thereby, vaporization of the boiler water in the boiler apparatus 5 can be promoted.

  FIG. 4 is a diagram showing a configuration of a boiler system 1a according to the second embodiment of the present invention. The boiler system 1a is used as an auxiliary boiler system for a relatively large ship, similarly to the boiler system 1 shown in FIG. 1, and heats the boiler water that is a medium by using the waste heat of the motor 2 with a supercharger. . In the boiler system 1a shown in FIG. 4, a boiler unit 50a having a different structure from the boiler unit 50 is provided instead of the boiler unit 50 shown in FIG. 1. The other structure of the boiler system 1a is the same as that of the boiler system 1 shown in FIG. 1, and the same code | symbol is attached | subjected to a corresponding structure in the following description.

  A boiler unit 50a shown in FIG. 4 includes a boiler body 51 that stores liquid boiler water. The boiler body 51 is provided on the exhaust path 32 of the prime mover 3 in the chimney of the ship, and the exhaust path 32 penetrates the boiler body 51. In other words, the boiler unit 50a is a so-called “composite boiler” provided in a chimney of a ship. The boiler unit 50a is a smoke tube type or water tube type boiler, and FIG. 2 will be described assuming that a smoke tube type boiler unit 50a is provided. In the boiler part 50 a, the exhaust passage 32 is branched into a plurality of thin tubes 321, and the plurality of thin tubes 321 penetrate from the bottom of the boiler body 51 toward the top. The plurality of thin tubes 321 are in direct contact with liquid boiler water stored in the boiler body 51. In the boiler part 50a, the boiler water in the boiler body 51 is heated by the exhaust of the prime mover 3 flowing through the plurality of thin tubes 321 of the exhaust passage 32, and steam of the boiler water is generated.

  In the boiler system 1a, as in the boiler system 1 shown in FIG. 1, in the heat storage mode, the boiler water sent from the boiler body 51 is guided to the heat storage unit 59 via the second circulation path 522, and the heat storage unit 59 After the heat storage material is heated (that is, after heat storage by the heat storage section 59 is performed), the heat storage material is heated by the compressed air heat exchanger 56 and returned to the boiler body 51. As shown in FIG. 5, in the heat supply mode, the boiler water sent from the boiler body 51 is guided to the heat storage unit 59 via the second circulation path 522 and heated by the heat storage material of the heat storage unit 59. After being done, it returns to the boiler body 51 of the boiler part 50a.

  As described above, the above-described heat storage unit 59, the second pump 55, and the second circulation path 522 are added to the boiler unit 50a that supplies steam to the steam system in the ship, similarly to the boiler system 1 shown in FIG. Thus, it is possible to provide the boiler system 1a having a simple structure that stores the waste heat of the prime mover 3 and heats the boiler water using the stored waste heat. Moreover, in the boiler system 1a, in the boiler part 50a, the structure of the boiler part 50a can be reduced in size by arrange | positioning the boiler main body 51 in the position (namely, inside the chimney of a ship) where the exhaust passage 32 penetrates. Thereby, the boiler system 1a can be reduced in size.

  FIG. 6 is a diagram showing a configuration of a boiler system 1b according to the third embodiment of the present invention. In the boiler system 1b, a recovery device 6 is provided in addition to the structure of the boiler system 1 shown in FIG. The other structure of the boiler system 1b is the same as that of the boiler system 1 shown in FIG. 1, and the same code | symbol is attached | subjected to a corresponding structure in the following description.

  As shown in FIG. 6, the recovery device 6 is disposed on a pipe that guides boiler water from the heat storage unit 59 to the boiler unit 50 on the second circulation path 522 of the boiler device 5. The recovery device 6 is a device that recovers energy from the boiler water sent from the heat storage unit 59 to the second circulation path 522. The recovery device 6 recovers thermal energy as power by an organic Rankine Cycle (ORC) using a working fluid having a lower boiling point than water (preferably, an organic medium such as alternative chlorofluorocarbon R245fa). is there. The recovery device 6 includes an ORC circuit 61, an ORC heat exchanger 62, an expander 63, a condenser 64, and an ORC pump 65. The ORC heat exchanger 62, the expander 63, the condenser 64, and the ORC pump 65 are connected in the above order by the ORC circulation path 61 through which the working fluid circulates.

  In the recovery device 6, the working fluid is pressurized by the ORC pump 65 and sent to the ORC heat exchanger 62. The ORC heat exchanger 62 is disposed on a pipe that guides boiler water from the heat storage unit 59 to the boiler unit 50 on the second circulation path 522. Specifically, the ORC heat exchanger 62 is disposed on the pipe through which the boiler water is guided from the heat storage unit 59 to the compressed air heat exchanger 56 in the second circulation path 522. In the ORC heat exchanger 62, the working fluid sent from the ORC pump 65 is heated and vaporized using boiler water flowing through the second circulation path 522 as a heat source. Moreover, the boiler water which flows through the 2nd circulation path 522 is cooled by the working fluid of the collection | recovery apparatus 6 in the ORC heat exchanger 62, and the temperature of boiler water falls.

  The working fluid heated and vaporized by the ORC heat exchanger 62 is guided to the expander 63 via the ORC circuit 61. The expander 63 expands the gaseous working fluid vaporized by the ORC heat exchanger 62 and recovers mechanical energy. As the expander 63, for example, a turbine rotated by a working fluid is used. The shaft of the turbine is connected to the generator 8, and the turbine 8 is driven by the working fluid sent from the ORC heat exchanger 62, whereby the generator 8 generates power.

  The gaseous working fluid that has passed through the expander 63 is guided to the condenser 64. The condenser 64 condenses and liquefies the working fluid expanded by the expander 63. The working fluid liquefied by the condenser 64 is pressurized as described above by the ORC pump 65 and sent to the ORC heat exchanger 62.

  In the boiler system 1b, as in the boiler system 1 shown in FIG. 1, in the heat storage mode, the boiler water sent from the boiler body 51 is guided to the heat storage unit 59 via the second circulation path 522, and the heat storage unit 59 The heat storage material is heated (that is, heat storage by the heat storage unit 59 is performed). The boiler water sent from the heat storage unit 59 passes through the ORC heat exchanger 62 of the recovery device 6, is heated by the compressed air heat exchanger 56, and returns to the boiler body 51. Further, as shown in FIG. 7, in the heat supply mode, the boiler water sent from the boiler body 51 is guided to the heat storage unit 59 through the second circulation path 522 and heated by the heat storage material of the heat storage unit 59. After being done, the boiler unit 50 returns to the boiler body 51.

  As described above, the above-described heat storage section 59, the second pump 55, and the second circulation path 522 are added to the boiler section 50 that supplies steam to the steam system in the ship, similarly to the boiler system 1 shown in FIG. Thus, it is possible to provide the boiler system 1b having a simple structure that stores the waste heat of the prime mover 3 and heats the boiler water using the stored waste heat.

  In the boiler system 1b, in the heat storage mode shown in FIG. 6, mechanical energy is generated from the boiler water sent from the heat storage unit 59 by the recovery device 6 including the ORC heat exchanger 62, the expander 63, the condenser 64, and the ORC pump 65. Can be recovered. Thereby, the waste heat of the motor | power_engine 3 collect | recovered with boiler water can be utilized efficiently. In addition, after the boiler water circulating in the second circulation path 522 is cooled in the ORC heat exchanger 62 of the recovery device 6, the waste water of the scavenging is converted into boiler water by heating in the compressed air heat exchanger 56 by scavenging. It can be recovered efficiently.

  FIG. 8 is a diagram showing a configuration of a boiler system 1c according to the fourth embodiment of the present invention. In the boiler system 1c, instead of the recovery device 6 shown in FIG. 6, a recovery device 6a having a partially different structure from the recovery device 6 is provided. The other structure of the boiler system 1c is the same as that of the boiler system 1b shown in FIG. 6, and the same code | symbol is attached | subjected to a corresponding structure in the following description.

  In the recovery device 6a, an expander 63a that is a two-stage turbine is provided instead of the expander 63 shown in FIG. The expander 63a includes a first expander 631 that is a high-pressure turbine and a second expander 632 that is a low-pressure turbine. Further, the recovery device 6a includes another ORC heat exchanger 62a and another ORC pump 65a in addition to the components of the recovery device 6 shown in FIG. In the following description, the ORC heat exchangers 62 and 62a are referred to as “first ORC heat exchanger 62” and “second ORC heat exchanger 62a”, respectively, in order to distinguish them. Further, in order to distinguish the ORC pumps 65 and 65a, they are referred to as “first ORC pump 65” and “second ORC pump 65a”, respectively.

  The second ORC pump 65 a is disposed on the piping between the first ORC pump 65 and the first ORC heat exchanger 62 in the ORC circuit 61. In the ORC circulation path 61, a branch portion 61a is provided between the first ORC pump 65 and the second ORC pump 65a, and a branch flow path 611 is branched from the ORC circulation path 61 in the branch portion 61a. A second ORC heat exchanger 62a is disposed on the branch flow path 611 from the branch portion 61a toward the expander 63a. The second ORC heat exchanger 62 a is disposed between the first ORC heat exchanger 62 and the compressed air heat exchanger 56 on the second circulation path 522 of the boiler device 5.

  In the recovery device 6a, the working fluid from the condenser 64 is pressurized by the first ORC pump 65 and sent to the branching portion 61a. A part of the working fluid delivered from the condenser 64 is branched into the branch flow path 611 at the branching portion 61a and led to the second ORC heat exchanger 62a. Further, the remaining portion of the working fluid is branched to the ORC circulation path 61 by the branching portion 61a, further pressurized by the second ORC pump 65a, and guided to the first ORC heat exchanger 62. The second ORC pump 65a is a pressure adjusting unit that makes the pressure of the working fluid guided to the first ORC heat exchanger 62 higher than the pressure of the working fluid guided to the second ORC heat exchanger 62a.

  In the first ORC heat exchanger 62, in the heat storage mode, the working fluid sent from the second ORC pump 65a is heated and vaporized using boiler water sent from the heat storage unit 59 and flowing through the second circulation path 522 as a heat source. The working fluid vaporized by the first ORC heat exchanger 62 is guided to the expander 63a and supplied to the first expander 631. On the other hand, the boiler water flowing through the second circulation path 522 is cooled by the working fluid of the recovery device 6a in the first ORC heat exchanger 62. The boiler water sent from the first ORC heat exchanger 62 is guided to the second ORC heat exchanger 62a.

  In the second ORC heat exchanger 62a, the boiler water sent from the first ORC heat exchanger 62 (that is, boiler water guided from the first ORC heat exchanger 62 to the compressed air heat exchanger 56) is used as a heat source, and the first ORC pump The working fluid delivered from 65 is heated and vaporized. As described above, since the pressure of the working fluid led to the second ORC heat exchanger 62a is lower than the pressure of the working fluid led to the first ORC heat exchanger 62, the evaporation temperature of the working fluid in the second ORC heat exchanger 62a Is lower than the evaporation temperature of the working fluid in the first ORC heat exchanger 62. The working fluid vaporized in the second ORC heat exchanger 62 a is guided to the expander 63 a and supplied to the second expander 632.

  On the other hand, the boiler water is cooled by the working fluid of the recovery device 6a in the second ORC heat exchanger 62a. The boiler water delivered from the second ORC heat exchanger 62a is guided to the compressed air heat exchanger 56, heated with the scavenging of the prime mover 3 as a heat source, and then returned to the boiler body 51.

  In the expander 63a of the recovery device 6a, the working fluid vaporized in the first ORC heat exchanger 62 expands in the first expander 631, and the expanded working fluid and vaporizes in the second ORC heat exchanger 62a. The working fluids that have been joined together in the second expander 632 are expanded. Then, the generator 8 generates power using the mechanical energy recovered by the expansion of the working fluid in the expander 63a.

  In the boiler system 1c, as in the boiler system 1b shown in FIG. 6, in the heat storage mode, the boiler water sent from the boiler body 51 is guided to the heat storage unit 59 via the second circulation path 522, and the heat storage unit 59 The heat storage material is heated (that is, heat storage by the heat storage unit 59 is performed). The boiler water sent from the heat storage unit 59 passes through the first ORC heat exchanger 62 and the second ORC heat exchanger 62a of the recovery device 6a, is heated by the compressed air heat exchanger 56, and is the boiler body 51 of the boiler unit 50. Return to. In addition, as shown in FIG. 9, in the heat supply mode, the boiler water sent from the boiler body 51 is guided to the heat storage unit 59 via the second circulation path 522 and heated by the heat storage material of the heat storage unit 59. After being done, the boiler unit 50 returns to the boiler body 51.

  As described above, the above-described heat storage unit 59, the second pump 55, and the second circulation path 522 are added to the boiler unit 50 that supplies the steam to the steam system in the ship, similarly to the boiler system 1b shown in FIG. Thus, it is possible to provide the boiler system 1c having a simple structure that stores the waste heat of the prime mover 3 and heats the boiler water using the stored waste heat.

  In the boiler system 1c, in the heat storage mode shown in FIG. 8, by increasing the evaporation temperature and pressure of the working fluid in the first ORC heat exchanger 62 of the recovery device 6a, the heat drop in the expander 63a can be increased. The energy recovery efficiency by the expander 63a can be improved. In addition, by lowering the evaporation temperature of the working fluid in the second ORC heat exchanger 62a to be lower than the evaporation temperature of the working fluid in the first ORC heat exchanger 62, it is possible to reduce the Heat can be recovered well. In the boiler device 5, the boiler water cooled in the first ORC heat exchanger 62 is further cooled in the second ORC heat exchanger 62a, whereby the difference between the scavenging temperature in the compressed air heat exchanger 56 and the temperature of the boiler water. Can be further increased. As a result, scavenging waste heat recovery efficiency in the compressed air heat exchanger 56 can be improved.

  Various modifications can be made in the above-described boiler systems 1 and 1a to 1c.

  The flow rate control unit 571 is not limited to a three-way valve, and for example, a circulation pump may be used as the flow rate control unit 571. Alternatively, even if an inverter pump capable of controlling the flow rate is used as the second pump 55 and the flow rate of boiler water flowing through the second circulation path 522 and returning to the boiler body 51 is controlled based on the temperature difference Δt described above. Good. In this case, the flow rate control part of the inverter pump is the flow rate control unit 571.

  The expanders 63 and 63a are not necessarily limited to turbines, and may be screw expanders, for example. In the boiler system 1 c shown in FIG. 7, a pressure reducing valve may be provided on the branch flow path 611 as a pressure adjusting unit instead of the second ORC pump 65 a.

  In the boiler unit 50 of the boiler systems 1, 1 b, and 1 c, the heat source for heating the boiler water flowing through the first circulation path 521 is not necessarily limited to the exhaust from the prime mover 3, and can be waste heat from the prime mover 3. Good. For example, boiler water flowing through the first circulation path 521 may be heated using the scavenging gas flowing through the scavenging path 31 as a heat source in a heat exchanger disposed on the scavenging path 31. In the boiler systems 1b and 1c, instead of the boiler unit 50, a boiler unit 50a shown in FIG. 4 may be provided.

  In the boiler systems 1 and 1a to 1c, the compressed air heat exchanger 56 and the switching unit 572 may be omitted. In this case, in both the heat storage mode and the heat supply mode, the boiler water sent from the heat storage unit 59 is directly guided to the flow rate control unit 571. Thereby, the structure of the boiler systems 1 and 1a-1c can be simplified.

  In the boiler systems 1 and 1a to 1c, various media such as heat transfer oil may be used instead of the boiler water. When heat transfer oil is used as a medium in the boiler apparatus 5 of the boiler systems 1, 1 a to 1 c, the medium vapor is not generated in the boiler apparatus 5, and the liquid heat transfer oil heated by the boiler apparatus 5 is It is used as a heating source for fuel oil, lubricating oil, and domestic water.

  The prime mover 3 may be a four-cycle diesel engine, for example. In this case, the compressed air that is the intake air pressurized by the compressor 42 is called “air supply”, and the scavenging path 31 is called an air supply path. The prime mover 3 may be an internal combustion engine other than a diesel engine or a prime mover other than the internal combustion engine. The prime mover 3 may be used for various purposes other than the main engine of the ship, and the boiler systems 1 and 1a to 1c may also be used for other uses other than the auxiliary boiler system of the ship.

  The configurations in the above-described embodiments and modifications may be combined as appropriate as long as they do not contradict each other.

1, 1a to 1c Boiler system 3 Motor 6, 6a Recovery device 32 Exhaust passage 50, 50a Boiler part 51 Boiler body 53 First pump 54 Exhaust heat exchanger 55 Second pump 56 Compressed air heat exchanger 59 Heat storage part 62 (first 1) ORC heat exchanger 62a 2nd ORC heat exchanger 63, 63a expander 64 condenser 65 (first) ORC pump 65a second ORC pump 511 compression unit 521 first circulation path 522 second circulation path 571 flow rate control section 573 temperature Difference acquisition unit

Claims (9)

A boiler system,
A boiler section for storing a liquid medium and heating the medium using waste heat from the prime mover as a heat source;
A pump for sending a liquid medium from the boiler unit and circulating it to the boiler unit via a circulation path;
Having a heat storage material, performing heat exchange between the heat storage material and the medium flowing through the circulation path, and performing heat storage by the heat storage material when the heat storage material is at a lower temperature than the medium flowing through the circulation path, A heat storage unit that heats the medium with the heat storage material when the heat storage material is hotter than the medium flowing through the circulation path;
A boiler system comprising: The boiler system according to claim 1,
The boiler section is
A boiler body for storing a liquid medium;
A liquid medium sent out from the boiler body, and another pump circulating through the other circulation path to the boiler body;
An exhaust heat exchanger for heating a medium flowing in the other circulation path using exhaust gas flowing in the exhaust path of the prime mover as a heat source;
A boiler system comprising: The boiler system according to claim 1,
The boiler unit includes a boiler body that stores a liquid medium and through which the exhaust passage passes,
The boiler system in which the medium in the boiler body is heated by the exhaust gas flowing through the exhaust passage. The boiler system according to any one of claims 1 to 3,
A compressed air heat exchanger that is arranged on a pipe that guides the medium from the heat storage unit to the boiler unit in the circulation path, and that heats the medium using compressed air that is pressurized intake air supplied to the prime mover as a heat source A boiler system characterized by further comprising: The boiler system according to any one of claims 1 to 4,
A temperature difference obtaining unit for obtaining a temperature difference obtained by subtracting the temperature of the heat storage material in the heat storage unit from the temperature of the medium in the boiler unit;
A flow rate control unit for controlling the flow rate of the medium guided from the heat storage unit to the boiler unit based on the temperature difference;
Further comprising
The boiler system, wherein the flow rate is reduced by the flow rate control unit as the temperature difference increases. The boiler system according to any one of claims 1 to 5,
A recovery device that is disposed on a pipe that guides a medium from the heat storage unit to the boiler unit in the circulation path, and that recovers energy from the medium sent from the heat storage unit;
The recovery device is
An ORC heat exchanger that heats and vaporizes the working fluid that is an organic medium using the medium flowing through the circulation path as a heat source;
An expander that expands the working fluid vaporized in the ORC heat exchanger and recovers mechanical energy;
A condenser that condenses and liquefies the working fluid expanded by the expander;
An ORC pump for delivering the working fluid liquefied in the condenser to the ORC heat exchanger;
A boiler system comprising: The boiler system according to any one of claims 1 to 6,
The medium is boiler water;
In the boiler unit, the boiler water steam is generated. The boiler system according to claim 7,
A boiler system, further comprising a steam compression section that compresses steam of boiler water sent out from the boiler section. The boiler system according to any one of claims 1 to 8,
The prime mover is a main engine of a ship;
The boiler system, wherein the boiler unit is an auxiliary boiler for the ship.

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