JP2007113424A - Cogeneration system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a cogeneration system which effectively feeds electric power and heat. <P>SOLUTION: A cogeneration system 100a feeds electric power outside by a generator 116 coupled to a stirling engine 110. A liquid flowing in through a first liquid inflow port 202 of a first liquid flow passage 200 in the cogeneration system 100a is fed to a first heat consuming device 300 after raising a temperature of the liquid by a cooler cooling part 130, a first latent heat exchanger 150 and a second latent heat exchanger 180. A liquid flowing in from an end 256 of a second liquid flow passage 250 is fed to a second heat consuming device 310 after raising a temperature of the liquid by a first sensible heat exchanger 140 and a second sensible heat exchanger 170. The cogeneration system 100a feeds heat outside through the utilization of the heat energy of sensible heat and latent heat of combustion gas produced by a first burner 120 and a second burner 160 and the heat produced by the cooler cooling part 130. By so doing, heat can be effectively fed to the outside. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a cogeneration system capable of supplying electric power using a Stirling engine to which a generator is connected, and supplying heat energy using heat generated when the Stirling engine is driven. .

A cogeneration system has been proposed that can supply power using a Stirling engine to which a generator is connected, and can supply heat energy using heat generated when the Stirling engine is driven. . The Stirling engine reciprocates the displacer and the piston by expanding and contracting a working fluid (for example, helium gas) before and after the displacer. The reciprocating motion of the piston is transmitted to the connected generator to generate electricity. A portion that expands the working fluid is referred to as a heater portion. Moreover, the part which contracts a working fluid is called a cooler part.
A burner is used to expand the working fluid in the heater section. This burner supplies heat energy to the outside using the heat of combustion gas generated by burning the fuel. Thus, electric power and heat energy can be supplied to the outside using the Stirling engine. Thermal energy supplied to the outside is often supplied to the outside as a high-temperature liquid having high thermal energy by raising the temperature of a low-temperature liquid by a heat exchanger using the heat of combustion gas.
Patent Document 1 discloses a cogeneration system using a Stirling engine to which a generator is connected.

WO01 / 090656

  The cogeneration system disclosed in Patent Document 1 includes a heat exchanger that exchanges heat between combustion gas and liquid in addition to a Stirling engine to which a generator is connected. The heat exchanger has a peak burner for raising the temperature of the fluid passing therethrough. In the technique of Patent Document 1, when the temperature of the liquid passing through the heat exchanger is raised with the combustion gas of the peak burner, the combustion gas of the burner that heats the heater portion of the Stirling engine is also guided to the heat exchanger. Increase efficiency.

In the technique of Patent Document 1, the combustion gas of the burner that heats the heater portion of the Stirling engine is guided to the heat exchanger to improve the efficiency of the heat exchanger. However, in the technique of Patent Document 1, since the combustion gas from the peak burner and the combustion gas from the burner that heats the heater of the Stirling engine are only used in one heat exchanger, both of the exhaust gas discharged from the heat exchanger are used. The temperature of the combustion gas is still higher than the atmospheric temperature. The thermal energy of the combustion gas discharged to the atmosphere is not effectively used.
A cogeneration system with further improved thermal efficiency is desired.

In the present invention, the thermal energy of the combustion gas of the burner that heats the heater section is recovered by the sensible heat exchanger and then recovered by another latent heat exchanger. By doing so, the thermal energy of the combustion gas of the burner which heats a heater part is collect | recovered efficiently. The recovered heat energy is used as a heat source for supplying heat energy to the outside of the cogeneration system.
The present invention succeeded in improving the efficiency of the cogeneration system by efficiently recovering the heat energy of the combustion gas of the burner that heats the heater part and using it as a heat source for supplying heat energy to the outside. .

The present invention can be embodied in a cogeneration system that supplies electric power and heat. The cogeneration system includes a Stirling engine having a heater unit and a cooler unit for reciprocating a displacer and a piston as well as a generator. Moreover, it arrange | positions in the upstream of the flow path of the 1st combustion gas produced by combustion of the 1st burner which heats the heater part of a Stirling engine, and heats a liquid with the heat | fever of a 1st combustion gas. The temperature of the liquid is increased by the condensation heat of the water vapor in the first combustion gas, which is disposed downstream of the first sensible heat exchanger and the flow path of the first combustion gas, and passes through the first sensible heat exchanger. A first latent heat exchanger is provided. A second sensible heat exchanger that is disposed upstream of a flow path of the second combustion gas generated by the combustion of the second burner and that heats the liquid by the heat of the second combustion gas; A second latent heat exchanger that is disposed downstream of the second combustion gas flow path and raises the temperature of the liquid by the condensation heat of water vapor in the second combustion gas that has passed through the second sensible heat exchanger. Prepare. Furthermore, the cooler cooling part which lets the liquid which cools the cooler part of a Stirling engine pass is provided. Furthermore, a first liquid channel and a second liquid channel are provided. The liquid inlet of the first liquid channel can be connected to the liquid outlet of the first heat consuming device, and the liquid outlet can be connected to the liquid supply port of the first heat consuming device. The first liquid channel guides the liquid flowing in from the liquid inlet to the liquid outlet after passing through the first latent heat exchanger, the second latent heat exchanger, and the cooler cooling unit. The second liquid channel is supplied with liquid from one end thereof, and the other end can be connected to the liquid supply port of the second heat consuming device. The second liquid flow path guides the supplied liquid to the other end that can be connected to the liquid supply port of the second heat consuming device after passing through the first sensible heat exchanger and the second sensible heat exchanger. .
The liquid here is typically water, but is not limited to water and may be liquid. In this specification, unless it is specifically stated as hot water or cold water, it is referred to as “water” or “liquid” regardless of whether it is hot water or cold water.
The first sensible heat exchanger and the first latent heat exchanger that raise the temperature of the liquid by the heat of the first combustion gas may be physically separated devices or may be integrated devices. . Similarly, the second sensible heat exchanger and the second latent heat exchanger that raise the temperature of the liquid by the heat of the second combustion gas may be physically separated devices or may be integrated devices. May be.
Further, the first latent heat exchanger, the second latent heat exchanger, and the cooler cooling unit may be connected to the first liquid channel in any order. Similarly, the first sensible heat exchanger and the second sensible heat exchanger may be connected to the second liquid flow path in any order.
In addition, the term “heat consuming device” as used in the present specification is used as a general term for heating devices that use thermal energy, such as floor heating devices, air conditioners, hot water supply devices, and heat exchange devices for reheating bathtub water. ing. Alternatively, the “heat consuming device” may be a device that consumes water and heat at the same time (that is, a device that consumes water having high thermal energy), such as a hot water tap or a hot water shower.

According to the said structure, electric power can be supplied to the exterior of a cogeneration system with the generator connected with the Stirling engine. On the other hand, the heat energy of the first combustion gas of the first burner that heats the heater portion of the Stirling engine, the heat energy of the second combustion gas of the second burner, and the heat energy absorbed from the cooler portion of the Stirling engine are used as heat sources. Heat can be supplied to the outside of the cogeneration system.
The heat energy of the first combustion gas generated by the combustion of the fuel gas by the first burner that heats the heater section of the Stirling engine is transferred to the heat exchanger by the first sensible heat exchanger and the first latent heat exchanger. Recovered into the passing liquid. Since the heat energy of the first combustion gas is recovered by the first sensible heat exchanger and the first latent heat exchanger, the first combustion gas eventually decreases to a temperature close to the atmospheric temperature. That is, most of the thermal energy of the first combustion gas can be recovered. Further, the heat energy of the second combustion gas generated by the combustion of the fuel gas by the second burner is recovered into the liquid passing through the heat exchanger by the second sensible heat exchanger and the second latent heat exchanger. Is done.

Furthermore, according to the said structure, when cooling the cooler part of a Stirling engine, the thermal energy absorbed from the cooler part is also collect | recovered to the liquid which passes a cooler cooling part. The heat energy recovered by the cooler is used as a heat source for heat energy supplied to the outside. Specifically, the first latent heat heat exchanger, the second latent heat heat exchanger, and the first liquid flow path for allowing the liquid to pass through the cooler cooling unit are provided. Moreover, the 2nd liquid flow path which lets a liquid pass to a 1st sensible heat exchanger and a 2nd sensible heat exchanger is provided. The sensible heat of the first combustion gas of the first burner and the sensible heat of the second combustion gas of the second burner are obtained by the first sensible heat exchanger and the second sensible heat exchanger arranged in the middle of the second liquid flow path. The thermal energy of heat is converted to the temperature of the liquid passing through the second liquid flow path. That is, the temperature of the liquid flowing through the second liquid channel is raised. Further, the heat of the latent heat of the first combustion gas and the second combustion gas after the sensible heat energy is recovered by the first latent heat exchanger, the second latent heat exchanger, the cooler cooling unit, and the first liquid flow path. The energy, and further, the thermal energy absorbed by the cooler cooling unit is converted to the temperature of the liquid passing through the first liquid channel. That is, the temperature of the liquid flowing through the first liquid channel is raised. Heat energy is supplied to the outside of the cogeneration system by supplying the heated water flowing out from the first liquid channel and the heated water flowing out from the second liquid channel to the heat consuming device.
The liquid flowing out from the liquid outlet of the first liquid channel is supplied to the first heat consuming device and gives thermal energy. By applying thermal energy to the first heat consuming device, the liquid having a low temperature is recirculated from the first heat consuming device to the liquid inlet of the first liquid channel. When all the heat energy of the liquid flowing out from the liquid outlet of the first liquid channel is not consumed by the first heat consuming device, the remaining heat energy is returned to the cogeneration system and heated up again. The thermal energy of the liquid flowing through the first liquid channel is not dissipated wastefully. The efficiency of the cogeneration system can be further improved.
As described above, in the cogeneration system of the present invention, most of the thermal energy generated by the first burner, the second burner, and the cooler cooling unit can be recovered. The efficiency of the cogeneration system can be improved.

The first liquid channel is preferably connected to a first heat consuming device operable with a liquid having a lower temperature than the second heat consuming device supplied with the liquid flowing through the second liquid channel.
Examples of the second heat consuming device include a bathroom heating device and a heat exchange device that heats water and supplies hot water. An example of the first heat consuming device is a floor heating device.
In addition, a plurality of first heat consuming devices operable with a liquid having a temperature lower than that of the second heat consuming device may be connected to the first liquid channel. Similarly, a plurality of second heat consuming devices that require liquid having a temperature higher than that of the first heat consuming device may be connected to the second flow path.

Heat consumption devices that use the heat supplied by the cogeneration system require devices that operate satisfactorily with relatively low-temperature liquids, such as floor heating, and relatively high-temperature liquids, such as hot water heat exchangers. There is a device to do.
On the other hand, the temperature of the liquid that has passed through the latent heat exchanger and the cooler cooling unit is lower than the temperature of the liquid that has been heated through the sensible heat exchanger.
Therefore, in the case of supplying heat to the outside, the first and second sensible heat exchangers arranged in the middle of the second liquid flow path are used for the second heat consuming device that requires a relatively high temperature liquid. To supply liquid that has become hot.
The first heat consuming device that operates sufficiently with the liquid having a temperature lower than that of the second heat consuming device passes the first and second latent heat exchangers arranged in the middle of the first liquid flow path, (2) Supply a liquid that is lower than the temperature of the liquid supplied to the heat consuming device but higher than room temperature. At this time, the amount of heat absorbed when cooling the cooler portion of the Stirling engine is also used to raise the temperature of the liquid passing through the first liquid flow path.
In the present invention, the first and second latent heat exchangers and the cooler cooling unit are connected to the first liquid channel. The first and second sensible heat exchangers are connected to the second liquid channel. The liquid passing through the second liquid flow path becomes higher temperature by the first and second sensible heat exchangers. The liquid that passes through the first liquid flow path by the first and second latent heat exchangers and the cooler cooling unit is lower in temperature than the liquid that has passed through the second liquid flow path but higher than room temperature. Taking advantage of the characteristics of the sensible heat exchanger and the latent heat exchanger, a liquid having a higher temperature and a liquid having a temperature lower than that and a temperature higher than normal can be supplied to the outside. Appropriate for each of the first heat consuming device that operates satisfactorily with liquid at a lower temperature than the second heat consuming device and the second heat consuming device that requires liquid at a higher temperature than the first heat consuming device. Temperature liquid can be supplied.

The first liquid channel may be arranged so that the liquid flowing in from the liquid inlet passes through the cooler cooling unit prior to the first latent heat exchanger and the second latent heat exchanger. Or the liquid which flows in from a liquid inflow port may be arrange | positioned so that it may pass a cooler cooling part, after passing a 1st latent heat heat exchanger and a 2nd latent heat heat exchanger.
In the former, the liquid having a low temperature given thermal energy to the first heat consuming device is passed through the cooler cooling unit prior to the first and second latent heat exchangers. The cooler can be cooled more efficiently. As a result, the power generation efficiency of the Stirling engine can be improved.
In the latter, the liquid which became low temperature by giving thermal energy to the first heat consuming device is passed through the first and second latent heat exchangers prior to the cooler cooling unit. By passing a low-temperature liquid through the two latent heat exchangers, the heat exchange efficiency of the two latent heat exchangers can be improved.
Alternatively, the liquid that has passed through one of the latent heat exchangers may then be passed through the cooler cooling unit and then passed through the other latent heat exchanger. It is possible to realize a cogeneration system that trades off both the power generation efficiency of the Stirling engine and the heat efficiency of the latent heat exchanger.
The order in which the first and second latent heat exchangers and the cooler cooling unit are arranged with respect to the first liquid flow path is determined by comparing the efficiency of the generator and the efficiency of the latent heat exchanger. What is necessary is just to set so that the efficiency of the whole generation system may become the highest.

  One end is branched from the first liquid channel at a portion closer to the liquid outlet than the first latent heat exchanger, the second latent heat exchanger, and the cooler cooling unit, and the other end is an end of the second liquid channel. It is preferable to further include a third liquid channel communicating with the end portion on the liquid supply side.

  With the third liquid channel, the liquid that has been heated through the first latent heat exchanger, the second latent heat exchanger, and the cooler cooling unit can be supplied to the second liquid channel. Since the temperature of the liquid supplied to the second liquid channel can be made higher than normal temperature, the liquid after passing through the first and second sensible heat exchangers arranged in the middle of the second liquid channel The temperature can be further increased. Alternatively, when the temperature of the liquid supplied to the second liquid channel is sufficiently high, the second sensible heat exchanger does not need to raise the temperature of the liquid passing therethrough much. That is, the output of the second burner that supplies the second combustion gas to the second sensible heat exchanger can be reduced. The efficiency of the cogeneration system can be further improved.

  One end can be connected to the liquid discharge port of the second heat consuming device, and the other end is connected to the first latent heat heat exchanger, the second latent heat heat exchanger, and the cooler cooling portion closer to the liquid inlet. It is preferable to further include a fourth liquid flow path communicating with the path.

  With the fourth liquid channel, the liquid discharged from the second heat consuming device can be refluxed to the portion of the first liquid channel close to the liquid inlet. Of the thermal energy of the liquid supplied from the second liquid channel to the second heat consuming device, the remaining heat energy not consumed by the second heat consuming device can be returned to the cogeneration system and reused. . The efficiency of the cogeneration system can be further increased.

  According to the present invention, electric power can be supplied by a generator connected to a Stirling engine. At the same time, the sensible heat and latent heat energy of the combustion gas generated by the first burner that heats the heater section of the Stirling engine, and the sensible heat and latent heat energy of the combustion gas generated by the second burner are recovered, and the cooler section The heat energy absorbed when cooling is also recovered and used as a heat source for the heat energy supplied to the outside. By doing so, the efficiency of the cogeneration system which supplies electric power and heat energy to the outside can be improved.

<First Embodiment>
An embodiment of the present invention will be described. FIG. 1 is a schematic diagram of a cogeneration system 100a according to the first embodiment of the present invention. In FIG. 1, parts that are necessary for practical use but are not necessary for explaining the configuration of the present embodiment, such as valves and fans, are not shown. For simplification, the cogeneration system 100a is hereinafter abbreviated as the cogeneration 100a.
The cogeneration unit 100a includes a Stirling engine 110, a first burner 120 that heats the heater unit 112 of the Stirling engine 110, a cooler cooling unit 130 that passes a liquid that cools the cooler unit 114 of the Stirling engine 110, and a first sensible heat exchange. , 140, first latent heat exchanger 150, second burner 160, second sensible heat exchanger 170, and second latent heat exchanger 180.
Further, the first liquid inlet 202 can be connected to the liquid outlet 302 of the first heat consuming device 300, the first liquid outlet 204 can be connected to the liquid supply port 304 of the first heat consuming device 300, A first liquid flow path that guides the liquid flowing in from the first liquid inlet 202 to the first liquid outlet 204 after passing through the cooler cooling unit 130, the first latent heat exchanger 150, and the second latent heat exchanger 180. 200.
Further, liquid is supplied from one end 256 (also referred to as second liquid flow path inlet 256), and the other end 254 (also referred to as second liquid outlet 254) is connected to the liquid supply port 314 of the second heat consuming device 310. The second liquid flow path 250 is provided that guides the supplied liquid to the second liquid outlet 254 after passing through the first sensible heat exchanger 140 and the second sensible heat exchanger 170.

  A generator 116 is connected to the Stirling engine 110. A Stirling engine 110 includes a displacer 118 and a piston 117 that can reciprocate. The displacer 118 and the piston 117 reciprocate by compressing and expanding the working fluid (for example, helium gas) in the heater unit 112 and the cooler unit 114 positioned before and after the displacer 118. The generator 116 is driven by the reciprocating motion of the piston 117 to generate power. The generated electric power is supplied to the outside of the cogeneration system 100a through the power lines 116a and 116b.

  The heater unit 112 of the Stirling engine 110 is heated by the combustion of fuel gas by the first burner 120 disposed adjacent to the heater unit 112. Further, the cooler unit 114 of the Stirling engine 110 is cooled by the liquid passing through the cooler cooling unit 130.

The first combustion gas generated when the first burner 120 burns the fuel gas passes through the first combustion gas flow path 122 and is discharged to the outside of the cogeneration system 100a as indicated by an arrow 121. A first sensible heat exchanger 140 is disposed on the upstream side of the first combustion gas passage 122 (that is, the side close to the first burner 120). Further, a first latent heat exchanger 150 is disposed on the downstream side of the first combustion gas flow path 122 (that is, the side far from the first burner 120).
The first sensible heat exchanger 140 performs heat exchange between the liquid passing through the first sensible heat exchanger 140 and the first combustion gas. That is, the temperature of the liquid passing through the first sensible heat exchanger 140 is raised. At that time, the heat energy transferred to the liquid is the sensible heat energy of the first combustion gas.
The first latent heat exchanger 150 performs heat exchange between the liquid passing through the first latent heat exchanger 150 and the first combustion gas after passing through the first sensible heat exchanger 140. That is, the temperature of the liquid passing through the first latent heat exchanger 150 is raised. At this time, the heat energy transferred to the liquid is the heat energy of the condensation heat released when the water vapor in the first combustion gas is condensed. Generally, a latent heat exchanger can recover thermal energy from a gas having a lower temperature than a sensible heat exchanger. Therefore, the first latent heat exchanger 150 can recover thermal energy from the first combustion gas whose temperature has decreased by the amount of sensible heat in the first sensible heat exchanger 140.

The relationship between the second combustion gas generated when the second burner 160 burns the fuel gas and the second sensible heat exchanger 170 and the second latent heat exchanger 180 is also the first sensible heat exchange with the first combustion gas. This is the same as the relationship between the heat exchanger 140 and the first latent heat exchanger 150. That is, the second combustion gas generated by the combustion of the second burner 160 is discharged to the outside of the cogeneration 100 a through the second combustion gas channel 162 as indicated by an arrow 161. A second sensible heat exchanger 170 is disposed on the upstream side of the second combustion gas flow path 162 (that is, the side close to the second burner 160). Further, a second latent heat exchanger 180 is disposed on the downstream side of the second combustion gas channel 162 (that is, the side far from the second burner 160).
In the second sensible heat exchanger 170, the temperature of the liquid passing through the inside is raised by the sensible heat energy of the second combustion gas.
In the second latent heat exchanger 180, the temperature of the liquid passing through the inside is raised by the heat energy of the latent heat of the second combustion gas after passing through the second sensible heat exchanger 170.
The second burner 160 further raises the temperature of the liquid heated by the first combustion gas generated by the first burner 120 and supplies a higher temperature liquid to the outside (that is, more heat energy is supplied to the outside). To supply).
Moreover, the 1st sensible heat exchanger 140 and the 1st latent heat exchanger 150 may be physically independent, and may be integrated. Similarly, the 2nd sensible heat exchanger 170 and the 2nd latent heat exchanger 180 may be physically independent, and may be integrated.

  On the other hand, in the cooler cooling unit 130 that cools the cooler unit 114 of the Stirling engine 110, the temperature of the liquid passing through the cooler cooling unit 130 is raised by the heat recovered from the working fluid that passes through the cooler unit 114.

Next, the first liquid channel 200 will be described. The cogeneration 100 a includes a first liquid outlet 204 for supplying a high-temperature liquid to the first heat consuming device 300. Moreover, the 1st liquid inflow port 202 which collect | recovers the liquid after giving thermal energy to the 1st heat consumption apparatus 300 again to the cogeneration 100a is provided.
The first liquid inlet 202 of the cogeneration 100 a is connected to the inlet 132 of the cooler cooling unit 130 by a pipe 210. The outlet 134 of the cooler cooling unit 130 is connected to the inlet 152 of the first latent heat exchanger 150 by a pipe 212. The outlet 154 of the first latent heat exchanger 150 is connected to the inlet 182 of the second latent heat exchanger 180 by a pipe 214. One end of a pipe 216 is connected to the outlet 184 of the second latent heat exchanger 180. The other end of the pipe 216 is a first liquid outlet 204 of the cogeneration 100a. The liquid flowing in from the inlet 132 of the cooler cooling unit 130 is heated in the cooler cooling unit 130 and flows out from the outlet 134. Similarly, the liquid flowing in from the inlet 152 of the first latent heat exchanger 150 is heated in the first latent heat exchanger 150 and flows out from the outlet 154. The same applies to the inlet 182 and the outlet 184 of the second latent heat exchanger 180.
The pipes 210, 212, 214, and 216 allow the liquid flowing in from the liquid inlet 202 of the cogeneration 100 a to pass through the cooler cooling unit 130, the first latent heat exchanger 150, and the second latent heat exchanger 180, and then A first liquid channel 200 that leads to one liquid outlet 204 is formed. A first pump 220 for causing the liquid in the first liquid flow path 200 to flow is arranged in the middle of the pipe 216.

  The first liquid outlet 204 of the cogeneration 100 a can be connected to the liquid supply port 304 of the first heat consuming device 300, and the first liquid inlet 202 of the cogeneration 100 a is the liquid outlet 302 of the first heat consuming device 300. Can be connected to. That is, in this embodiment, the cogeneration 100 a can supply a high-temperature liquid to the first heat consuming device 300 from the first liquid outlet 204. That is, the cogeneration 100a can supply heat energy to the outside using a high-temperature liquid as a medium. The first heat consuming device 300 is, for example, a floor heating device. The liquid whose temperature is lowered by applying thermal energy to the floor heating device flows from the first liquid inlet 202 into the cogeneration system 100a.

Next, the second liquid channel 250 will be described. In addition to the first liquid outlet 204, the cogeneration 100a includes a second liquid outlet 254 for supplying a high-temperature liquid to the outside.
One end of a pipe 260 is connected to the inlet 142 of the first sensible heat exchanger 140. As shown by an arrow 272, normal temperature water is supplied from the outside from the other end 256 (second liquid flow path inlet 256) of the pipe 260. The outlet 144 of the first sensible heat exchanger 140 is connected to the inlet 172 of the second sensible heat exchanger 170 by a pipe 262. One end of a pipe 264 is connected to the outlet 174 of the second sensible heat exchanger 170. The other end of the pipe 264 is the second liquid outlet 254 of the cogeneration 100a. The inlet 142 and outlet 144 of the first sensible heat exchanger 140 and the inlet 172 and outlet 174 of the second sensible heat exchanger 170 are the same as those when the first liquid channel 200 is described. This is the same as the inlet 152 and the outlet 154 of the single latent heat exchanger 150.

After normal temperature water supplied from the second liquid flow path inlet 256 of the pipe 260 is passed through the first sensible heat exchanger 140 and the second sensible heat exchanger 170 by the pipes 260, 262, 264. A second liquid channel 250 leading to the second liquid outlet 254 is formed. A second pump 270 for causing the liquid in the second liquid channel 250 to flow is disposed in the middle of the pipe 260.
The second liquid outlet 254 can be connected to the liquid supply port 314 of the second heat consuming device 310. That is, the cogeneration 100 a can supply a high-temperature liquid to the second heat consuming device 310 from the second liquid outlet 254. The cogeneration system 100a can supply heat energy to the outside from the first liquid outlet 202 described above, and can also supply heat energy to the outside from the second liquid outlet 254. The second heat consuming device 310 is, for example, an air conditioner or a hot water supply device.

Next, the operation of the cogeneration 100a will be described. In the cogeneration system 100a, the generator 116 is driven by the Stirling engine 110 to supply power to the outside. Hereinafter, the operation when the cogeneration 100a supplies heat energy to the outside will be described by exemplifying the temperature change of the liquid passing through the first liquid channel 200 and the second liquid channel 250.
Now, it is assumed that the temperature of the liquid discharged from the first heat consuming apparatus 300 is 25 ° C. In the cooler cooling unit 130 into which the liquid at 25 ° C. flows, the temperature of the passing liquid is raised by the thermal energy obtained when the cooler unit 114 of the Stirling engine 110 is cooled. The temperature of the liquid at the outlet of the cooler cooling unit 130 is, for example, 30 ° C. Next, in the first latent heat exchanger 150 into which the liquid heated to 30 ° C. flows, the temperature of the passing liquid is raised by the latent heat of the first combustion gas generated by the first burner 120. As a result, the temperature of the liquid at the outlet of the first latent heat exchanger 150 is 40 ° C., for example. Similarly, when the liquid at 40 ° C. passes through the second latent heat exchanger 180, the temperature is raised by the latent heat of the second combustion gas to, for example, 50 ° C. The liquid at 25 ° C. that flows in from the first liquid inlet 202 is heated to 50 ° C., led to the first liquid outlet 204, and again receives the first heat through the liquid supply port 314 of the first heat consuming device 300. It is supplied to the consumption device 300. In this way, the cogeneration system 100 a raises the temperature of the liquid passing through the first liquid flow path 200 by the cooler cooling unit 130, the first latent heat exchanger 150, and the second latent heat exchanger 180, and rises to the first heat consuming device 300. Supplying a warmed liquid (i.e. the thermal energy that the liquid has).

  On the other hand, it is assumed that the temperature of the liquid flowing in from the second liquid channel inlet 256 of the second liquid channel 250 is 10 ° C., for example. 10 ° C. is the temperature of the liquid at room temperature. In the first sensible heat exchanger 140 into which the liquid at 10 ° C. flows, the temperature of the passing liquid is raised by the sensible heat of the first combustion gas generated by the first burner 120. As a result, the temperature of the liquid at the outlet of the first sensible heat exchanger 140 is 40 ° C., for example. Similarly, the temperature of the liquid at 40 ° C. is raised by the sensible heat of the second combustion gas when passing through the second sensible heat exchanger 170 and becomes, for example, 70 ° C. The liquid at a room temperature of 10 ° C. flowing in from the second liquid channel inlet 256 of the second liquid channel 250 is heated to 70 ° C. and guided to the second liquid outlet 254, and the liquid supply of the second heat consuming device 310 is performed. It is supplied to the second heat consuming device 310 through the port 314. In this way, the cogeneration system 100a raises the temperature of the liquid passing through the second liquid flow path 250 by the first sensible heat exchanger 140 and the second sensible heat exchanger 170, and the temperature is raised to the second heat consuming device 310. A liquid (ie, heat energy that the liquid has) is supplied.

As described above, in the cogeneration system 100a, the first combustion gas generated by the first burner 120 by the first sensible heat exchanger 140 and the second sensible heat exchanger 170 disposed in the middle of the second liquid flow path 250. The sensible heat energy of sensible heat and the sensible heat energy of the second combustion gas generated by the second burner 160 can be converted into a liquid, and the heat energy can be supplied to the outside using the heated liquid as a medium.
Further, the first latent heat heat exchanger 150 and the second latent heat exchanger 180 arranged in the middle of the first liquid flow path 200 and the second heat energy of the first combustion gas generated by the first burner 120 and the second The heat energy of the latent heat of the second combustion gas generated by the burner 160 can be converted into a liquid, and the heat energy can be supplied to the outside using the heated liquid as a medium. At this time, the heat energy recovered from the cooler 114 of the Stirling engine 110 is also converted into a liquid that passes through the first liquid flow path 200.
As described above, the cogeneration system 100a has the sensible heat and latent heat energy of the first combustion gas generated by the first burner 120, the sensible heat and latent heat energy of the second combustion gas generated by the second burner 160, and The heat energy obtained from the cooler unit 114 of the Stirling engine 110 can be recovered, and the recovered heat energy can be supplied to the outside. By doing so, the cogeneration 100a with improved thermal efficiency can be realized.

Here, the first liquid channel 200 is connected to the first heat consuming device 300 operable with a liquid having a lower temperature than the second heat consuming device 310 to which the liquid flowing through the second liquid channel 250 is supplied. It is preferable. An example of the first heat consuming device is a floor heating device. Examples of the second heat consuming device include an air conditioner and a hot water supply device.
The liquid flowing through the first liquid flow path 200 is heated by the cooler cooling unit 130, the first latent heat exchanger 150, and the second latent heat exchanger 180. On the other hand, the temperature of the liquid flowing through the second liquid flow path 250 is raised by the first sensible heat exchanger 140 and the second sensible heat exchanger 170. Due to the difference in characteristics between the sensible heat exchanger and the latent heat exchanger, the temperature of the liquid that can be supplied from the first liquid channel 200 to the outside is higher than the temperature of the liquid that can be supplied from the second liquid channel 250 to the outside. Low. Taking advantage of the characteristics of the sensible heat exchanger and the latent heat exchanger, each of the first heat consuming device 300 that operates sufficiently with a low temperature liquid and the second heat consuming device 310 that requires a high temperature liquid, respectively. On the other hand, a liquid having an appropriate temperature can be supplied. The heat supplied by the cogeneration 100a can be used efficiently.

Further, the order in which the liquid flowing through the first liquid flow path 200 passes through the cooler cooling unit 130, the first latent heat exchanger 150, and the second latent heat exchanger 180 may be any order. Different effects can be obtained depending on the order.
For example, it arrange | positions so that the liquid which flows through the 1st liquid flow path 200 may pass the cooler cooling part 130 ahead of the 1st latent heat exchanger 150 and the 2nd heat exchanger 180. FIG. By doing so, a cooler liquid can be passed through the cooler cooling unit 130. The cooler 114 of the Stirling engine 110 can be cooled more efficiently. As a result, the power generation efficiency of the power generator 116 connected to the Stirling engine 110 can be improved.
Further, for example, the liquid flowing through the first liquid flow path 200 is disposed so as to pass through the cooler cooling unit 130 after passing through the first latent heat exchanger 150 and the second heat exchanger 180. By doing so, the cooler liquid can be passed through the two latent heat exchangers 150, 180. As a result, the heat exchange efficiency in the two latent heat exchangers 150 and 180 can be improved.
Also, for example, the liquid that has passed through one of the two latent heat exchangers 150 and 180 is then passed through the cooler cooling unit 130 and then the other latent heat exchanger is passed through. May be. A cogeneration system 100a that trades off both the power generation efficiency of the power generator 116 and the heat efficiency of the latent heat exchangers 150 and 180 can be realized.
The order of passing the liquid flowing through the first liquid channel 200 through the two latent heat exchangers 150 and 180 and the cooler cooling unit 130 depends on the efficiency of the generator 116 and the efficiency of the latent heat exchanger. What is necessary is just to set so that the efficiency of the whole cogeneration 100a may become the highest compared.

Second Embodiment
Next, a second embodiment of the present invention will be described. FIG. 2 is a schematic diagram of a cogeneration system 100b according to the second embodiment. Hereinafter, in order to simplify the description, the cogeneration system 100b is referred to as a cogeneration system 100b. In addition to the cogeneration 100 a shown in FIG. 1, the cogeneration 100 b includes a first liquid flow than the cooler cooling unit 130, the first latent heat exchanger 150, and the second latent heat exchanger 180 in the first liquid flow path 200. A pipe 280 that communicates between a branch point 272 near the outlet 204 and the second liquid channel inlet 256 of the second liquid channel 250 is provided. This pipe 280 is referred to as a third liquid channel.
Furthermore, in addition to the cogeneration 100a shown in FIG. 1, one end 274 (also referred to as a second liquid inlet 274) can be connected to the liquid outlet 312 of the second heat consuming device 310b, and the other end is the first liquid channel. 200, a pipe communicating with the confluence 276 of the first liquid flow path 200 in a portion closer to the first liquid inlet 202 than the cooler cooling unit 130, the first latent heat exchanger 150, and the second latent heat exchanger 180. 278. This pipe 278 is referred to as a fourth liquid channel 278.
Note that the same devices and parts as those of the cogeneration system 100a shown in FIG. 1 are denoted by the same reference numerals in FIG.

The operation when the cogeneration 100b to which the third liquid channel 280 and the fourth liquid channel 278 are added supplies heat energy to the outside includes the first liquid channel 200 and the second liquid channel 250. The temperature change of the liquid passing through each liquid flow path will be described as an example.
The third liquid channel 280 branched from the branch point 272 of the first liquid channel 200 is connected to the second liquid channel inlet 256 at the end of the second liquid channel 250. Accordingly, a part of the liquid heated by passing through the cooler cooling unit 130, the first latent heat exchanger 150, and the second latent heat exchanger 180 is added to the second liquid channel 250 by the third liquid channel 280. 2 liquid channel inlet 256 is supplied. Now, it is assumed that the temperature of the liquid that has passed through the cooler cooling unit 130, the first latent heat exchanger 150, and the second latent heat exchanger 180 is 55 ° C., for example. The reason why the temperature of the liquid that has passed through the cooler cooling unit 130, the first latent heat exchanger 150, and the second latent heat exchanger 180 is higher than the temperature 50 ° C. in the same place shown in FIG. 1 will be described later. In the cogeneration system 100a shown in FIG. 1, the temperature of the liquid supplied to the second liquid channel inlet 256 of the second liquid channel 250 is 10 ° C., which is normal temperature. On the other hand, in the cogeneration system 100b, the liquid at 55 ° C. is supplied to the second liquid channel 250 by the third liquid channel 280. Therefore, in the first sensible heat exchanger 140, the flowing 55 ° C. liquid can be heated to 70 ° C., for example. Furthermore, in the 2nd sensible heat exchanger 170, the 70 degreeC liquid which flows in can be heated up to 85 degreeC, for example. As a result, the liquid heated to 85 ° C. can be supplied to the second heat consuming device 310. The temperature of the liquid supplied to the 2nd heat consuming apparatus 310 can be made into a liquid higher temperature than the cogeneration 100a of FIG.

  In addition, the liquid discharged from the liquid discharge port 312 of the second heat consuming device 310 b flows into the cogeneration 100 b from the second liquid inlet 274 and is joined by the fourth liquid channel 278 to the first liquid channel 200. In 276, the liquid discharged from the first heat consuming apparatus 300 is merged. The second heat consuming device 310b is a device that requires a liquid having a temperature higher than that of the first heat consuming device 300. In this case, the temperature of the liquid discharged from the liquid discharge port 312 after supplying thermal energy to the second heat consuming device 310 b is discharged from the liquid discharge port 302 after supplying thermal energy to the first heat consuming device 300. Often higher than the temperature of the liquid. The temperature of the liquid merged at the merge point 276 of the first liquid flow path 200 and the fourth liquid flow path 278 is higher than the temperature of the liquid discharged from the fluid discharge port 302 of the first heat consuming apparatus 300. It is assumed that the temperature of the liquid after joining at this time is 30 ° C., for example. This temperature of 30 ° C. is higher than the temperature of 25 ° C. of the liquid flowing into the cooler cooling unit 130 in the cogeneration system 100a shown in FIG. Therefore, in the cooler cooling unit 130, the flowing 30 ° C. liquid can be heated to 35 ° C., for example. Further, in the first latent heat exchanger 150, the flowing 35 ° C. liquid can be heated to 45 ° C., for example. Further, in the second latent heat exchanger 180, the flowing 45 ° C. liquid can be heated to 55 ° C., for example. As a result, the liquid heated to 55 ° C. can be supplied to the first heat consuming apparatus 300. The temperature of the liquid supplied to the 1st heat consumption apparatus 300 can be made into a liquid higher temperature than the cogeneration 100a of FIG.

  As described above, in the cogeneration system 100b, the liquid that has been heated by passing through the cooler cooling unit 130, the first latent heat exchanger 150, and the second latent heat exchanger 180 is supplied to the second liquid channel 280 by the second liquid channel 280. The liquid can be supplied to the liquid channel 250. Since the temperature of the liquid supplied to the second liquid channel 250 can be made higher than the normal temperature, the first sensible heat exchanger 140 and the second sensible heat exchanger 170 are passed through the second liquid channel 250. The temperature of the later liquid can be further increased. Alternatively, since the temperature of the liquid supplied to the second liquid channel 250 can be made higher than the normal temperature, the sensible heat energy of the second combustion gas for raising the temperature of the liquid by the second sensible heat exchanger 170. Can be reduced. In other words, the fuel consumed by the second burner 160 can be reduced.

  Further, the liquid discharged from the second heat consuming device 310b can be recirculated to the portion of the first liquid channel 200 close to the liquid inlet 202 by the fourth liquid channel 278. Of the thermal energy of the liquid supplied from the second liquid channel 250 to the second heat consuming device 310b, the remaining heat energy that is not consumed by the second heat consuming device 310b is used again for the first liquid channel 200 of the cogeneration 100b. Can be reused. The efficiency of the cogeneration 100b can be further increased.

As described above, in the embodiment of the present invention described with reference to FIGS. 1 and 2, the sensible heat and latent heat energy of the first combustion gas generated by the first burner 120 for heating the heater unit 112 of the Stirling engine 110, The sensible heat and latent heat energy of the second combustion gas generated by the two-burner 160 and the heat energy recovered from the cooler 114 of the Stirling engine 110 are used to supply heat to the outside. By doing so, it is possible to realize a cogeneration system that efficiently uses the thermal energy generated when the Stirling engine 110 is driven and the thermal energy generated by the second burner.
In the embodiment of the present invention described with reference to FIGS. 1 and 2, a second liquid channel 250 that supplies heat energy to the outside using a high-temperature liquid as a medium, and a liquid that is supplied by the second liquid channel 250. A first liquid channel 200 is provided that supplies heat energy to the outside using a liquid that is at a lower temperature but higher than the normal temperature as a medium. That is, the cogeneration systems 100a and 100b can supply liquids having different temperatures to the outside. The liquid of the temperature suitable for each heat consumption apparatus can be supplied with respect to the several heat consumption apparatus from which the temperature of the required liquid differs. There is no need for an additional device such as a temperature control device for adjusting the temperature of the liquid supplied by the cogeneration system to the temperature of the liquid required by the heat consuming device.
In the embodiment of the present invention described with reference to FIGS. 1 and 2, the first heat consuming device 300 and the second heat consuming devices 310 and 310b are devices outside the cogeneration units 100a and 100b. However, for example, when a hot water supply device or the like is used as the second heat consuming device 310, a part or all of the hot water supply device such as a heat exchanger may be added to a part of the configuration of the cogeneration systems 100a and 100b.
1 and 2, only one first heat consuming device 300 is illustrated as the heat consuming device connected to the first liquid channel 200 of the cogeneration 100a, 100b. A plurality of first heat consuming devices may be connected to the. Similarly, in FIG. 1, only one second heat consuming device 310 is drawn as the heat consuming device connected to the second liquid flow path 250 of the cogeneration 100a, and in FIG. 2, the second liquid flow of the cogeneration 100a is drawn. Although only one second heat consuming device 310b is drawn as the heat consuming device connected to the channel 250, a plurality of second heat consuming devices may be connected to the second liquid channel 250.

In the embodiment described with reference to FIGS. 1 and 2, a part of the liquid heated by the first sensible heat exchanger 140 and the second sensible heat exchanger 170 is converted into the cooler cooling unit 130 and the first latent heat. The liquid heated by the heat exchanger 150 and the second latent heat exchanger 180 may be merged and supplied to the first heat consuming apparatus 300. Specifically, for example, a cistern is provided in the middle of the pipe 216 constituting a part of the first liquid channel 210. A pipe that branches from the middle of a pipe 264 that constitutes a part of the second liquid flow path 250 and guides the liquid flowing through the second liquid flow path 250 to the cis turn is disposed in the systern.
By providing the pipe that leads to the cistern, the liquid that has passed through the first sensible heat exchanger 140 and the second sensible heat exchanger 170 can be guided to the first liquid flow path 200 through the cistern. it can. By doing so, for example, when the second heat consuming device 310b has stopped operating, or when the amount of heat consumed by the second heat consuming device 310b is small, the first sensible heat exchanger 140 and the second sensible heat exchanger 140b are used. The liquid whose temperature has been raised by the heat heat exchanger 170 can be supplied to the first heat consuming device 300 via a cistern. A configuration obtained by adding the above-described cistern or the like to the configuration of the second embodiment shown in FIG.
The temperature values of the liquid illustrated in FIGS. 1 and 2 are values temporarily illustrated to explain the operation of the cogeneration units 100a and 100b. Actually, the burners 120 and 160 and the two sensible heat exchangers are used. Needless to say, it changes depending on the heat exchange efficiency of 140 and 170 and the two latent heat exchangers 150 and 180.

An embodiment embodying a cogeneration system of the present invention will be described with reference to the drawings. FIG. 3 shows the configuration of the cogeneration system 1000 of the present embodiment.
The cogeneration system 1000 of the present embodiment is based on the second embodiment shown in FIG. 2 with various parts that are actually necessary. Further, for convenience of drawing, different names may be given to the components of the cogeneration system of the present example of FIG. 3 corresponding to the components of the cogeneration system shown in the second embodiment of FIG. First, the correspondence between the cogeneration system 1000 of the present embodiment and the cogeneration system 100b of the second embodiment shown in FIG. 2 will be described. In FIGS. 1 and 2, the flow path of the fluid is shown by a white line, but in FIG. 3, the flow path of the fluid is drawn by a single line in order to simplify the drawing.

The cogeneration system 1000 of this embodiment mainly includes a power generation device 1002, a first combustion device 1006, a second combustion device 1044, a cistern 1020, a low temperature heater 1032, a high temperature heater 1074, and a water heater 1100. And a bath water heater 1130. Here, the low-temperature heater 1032 is a floor heater. The high temperature heater 1074 is a bathroom heater. The temperature of the liquid passed to the floor heater may be lower than the temperature of the liquid passed to the bathroom heater. Therefore, the floor heater is referred to as a low-temperature heater 1032, and the bathroom heater is referred to as a high-temperature heater 1074. That is, the “low temperature heater” means a heater that operates sufficiently with water having a lower temperature than the “high temperature heater”. The bath water heater 1130 has a function of supplying hot water to fill the bathtub 1132 and a function of chasing the bathtub water.
Note that the low-temperature heater 1032, the high-temperature heater 1074, the water heater 1100, and the bath water heater 1130 may be external devices that can be connected to the cogeneration system 1000, but here, the overall configuration is easily described. Therefore, these devices are collectively referred to as a cogeneration system 1000.
In the power generation apparatus 1002, a Stirling engine 110 and a first combustion apparatus 1006 are arranged. A generator 116 is connected to the Stirling engine 110. The Stirling engine 110 has a heater portion 112 and a cooler portion (not shown in FIG. 3; see FIG. 1). Adjacent to the cooler part of the Stirling engine 110, a cooler cooling part 130 for cooling the cooler part is arranged.

Inside the first combustion apparatus 1006, a first burner 120, a first sensible heat exchanger 140, a first latent heat exchanger 150, and a suction fan 1018 are arranged. The flow path of the combustion gas formed by the inner wall of the first combustion device 1006 corresponds to the first gas combustion gas flow path 122 shown in the second embodiment of FIG. That is, as shown in FIG. 3, in the first combustion device 1006, the upstream side of the gas flow path (first combustion gas flow path 122) formed by the inner wall of the first combustion apparatus 1006 (that is, in the first burner 120. The first sensible heat exchanger 140 is disposed on the near side, and the first latent heat exchanger 150 is disposed on the downstream side (that is, the side far from the first burner 120).
The second combustion device 1044 includes a second burner 160, a second sensible heat exchanger 170, a second latent heat exchanger 180, and a blower fan 1052. The flow path of the combustion gas formed by the inner wall of the second combustion device 1044 corresponds to the second gas combustion gas flow path 162 shown in the second embodiment of FIG. That is, as shown in FIG. 3, in the second combustion device 1006, the upstream side of the gas flow path (second combustion gas flow path 162) formed by the inner wall of the second combustion apparatus 1044 (that is, the second burner 160). The second sensible heat exchanger 170 is disposed on the near side, and the second latent heat exchanger 180 is disposed on the downstream side (that is, the side far from the second burner 160).
Further, in FIG. 3, flow paths for connecting the heat exchangers, the low-temperature heater 1032, the high-temperature heater 1074, and the like and flowing a liquid between them are drawn. In addition, the liquid which flows through the flow path of the cogeneration system 1000 of the present embodiment is water. The flow path includes a flow path through which high-temperature water flows, and a flow path through which low-temperature water and cold water flow.

The flow path 200 shown by the thickest black line in FIG. 3 corresponds to the first liquid flow path 200 shown in the second embodiment of FIG. The specific correspondence is as follows.
Of the end portions of the first cold water passage 1038 in FIG. 3, one end on the side connected to the junction 1500 corresponds to the first liquid inlet 202 shown in the second embodiment in FIG. Starting from the merge point 1500, the first cold water channel 1038 connected to the merge point 1500, the flow path in the cooler cooling unit 130 connected to the other end of the first cold water channel 1038, and the cooler cooling unit 130 A second cold water passage 1040 connected to the flow passage outlet, a flow passage of the first latent heat exchanger 150 connected to the other end of the second cold water passage 1040, and a flow passage of the first latent heat heat exchanger 150 A third cold water path 1042 connected to the outlet, a flow path of the second latent heat exchanger 180 connected to the other end of the third cold water path 1042, and a flow path outlet of the second latent heat heat exchanger 180. The flow path formed by the connected systern return path 1054 and the other end of the systern return path 1054 and the systern forward path 1024 communicating with the other end of the systern 1020 is the first liquid path shown in the second embodiment of FIG. 200 vs. To. Then, one end on the side connected to the branch point 1502 in the end of the cistern forward path 1024 in FIG. 3 corresponds to the first liquid outlet 204 shown in the second embodiment in FIG. 2.

A flow path 250 indicated by a thick black line in FIG. 3 corresponds to the second liquid flow path 250 shown in the second embodiment of FIG. The specific correspondence is as follows.
The inlet 1504 of the first sensible heat exchanger 140 in FIG. 3 corresponds to the second liquid flow path inlet 256 shown in the second embodiment in FIG. Starting from the inlet 1504 of the first sensible heat exchanger 140, the second hot water passage 1056 connected to the flow path of the first sensible heat exchanger 140 and the flow path outlet of the first sensible heat exchanger 140. And a second sensible heat exchanger 170 connected to the other end of the second hot water passage 1056, and a third hot water passage 1058 connected to the flow path outlet of the second sensible heat exchanger 170. The flow path corresponds to the second liquid flow path 250 shown in the second embodiment of FIG. And one end of the end part of the 3rd warm water channel 1058 of FIG. 3 connected to the branch point 1506 respond | corresponds to the 2nd liquid outflow port 254 shown in 2nd Embodiment of FIG.

3 corresponds to the third liquid channel 280 shown in the second embodiment of FIG. 2. The first hot water channel 1030 connecting the branch point 1502 shown in FIG. 3 and the inlet 1504 of the first sensible heat exchanger 140.
Furthermore, the return path 1078 connecting the junction 1508 and the junction 1500 shown in FIG. 3 corresponds to the fourth liquid channel 278 shown in the second embodiment of FIG.

Further, in the cogeneration system 1000 of the present example, hot water flows from the branch point 1502 corresponding to the first liquid outlet 204 shown in the second embodiment of FIG. 2 to the low temperature heater 1032 via the low temperature heating forward path 1028. Supplied. Further, the water whose temperature has been reduced by applying thermal energy to the low-temperature heater 1032 flows into the junction 1500 corresponding to the first liquid inlet 202 shown in the second embodiment of FIG. . That is, the low-temperature heater 1032 corresponds to the first heat consuming apparatus 300 shown in FIG.
Furthermore, in the cogeneration system 1000 of the present embodiment, from the branch point 1506 corresponding to the second liquid outlet 254 shown in the second embodiment of FIG. 2 to the high temperature heater 1074, the hot water heater 1100, and the bath water heater 1130. Hot hot water is supplied. Then, the water whose temperature is lowered by applying thermal energy to the high-temperature heater 1074, the hot water heater 1100, and the bath water heater 1130 is the junction 1508 corresponding to the second liquid inlet 274 shown in the second embodiment of FIG. Flows into. That is, each of the high temperature heater 1074, the hot water heater 1100, and the bath water heater 1130 corresponds to the second heat consuming device 310b shown in the second embodiment of FIG.

Next, the structure of each part of the cogeneration system 1000 of the present embodiment will be specifically described.
The Stirling engine 110 of the power generation device 1002 heats the heater unit 112 with the first combustion device 1006 and cools the cooler unit (see FIG. 1) with the cooler cooling unit 130, thereby disposing the displacer and piston inside (see FIG. 1). Reciprocates. The generator 116 generates electricity by transmitting the reciprocating motion of the piston to the generator 116. The electric power generated by the generator 116 is transmitted to the grid box 1010 in FIG.

  The first combustion device 1006 includes a first burner 120, a first sensible heat exchanger 140, a first latent heat exchanger 150, and a suction fan 1018. The first burner 120 heats the heater unit 112 of the Stirling engine 110 with the combustion gas. The first sensible heat exchanger 140 is a heat transfer tube that passes through the inside of the first combustion device 1006, and performs heat exchange between water that passes through the inside of the heat transfer tube and combustion gas that flows outside the heat transfer tube. The first latent heat exchanger 150 is a heat transfer tube that passes through the inside of the first combustion device 1006, and performs heat exchange between water that passes through the inside of the heat transfer tube and combustion gas that flows outside the heat transfer tube. Since low temperature water passes through the inside of the first latent heat exchanger 150, water vapor contained in the combustion gas flowing outside condenses on the surface of the first latent heat exchanger 150. Water flowing through the first latent heat exchanger 150 is heated by the condensation heat of the water vapor at this time. The combustion gas supplied from the first burner 120 heats the heater portion 112 of the Stirling engine 110 and is then sucked by the suction fan 1018 and passes through the first sensible heat exchanger 140 and the first latent heat exchanger 150. And discharged to the outside.

  The cooler cooling unit 130 includes a flow path through which water flows, and heat exchange is performed between the water flowing through the flow path and the working fluid passing through the cooler section (not shown in FIG. 3) of the Stirling engine 110. Do. Since low-temperature water flows through the cooler cooling unit 130, the working fluid passing through the cooler unit (not shown) of the Stirling engine 110 is cooled.

  The cistern 1020 is a tank for storing water (hot water). In the cistern 1020, water level electrodes 1020a and 1020b are mounted. The lower end of the water level electrode 1020a is located at the high level water level of the cistern 1020. The lower end of the water level electrode 1020b is located at the low level water level of the cistern 1020. The water level electrode 1020a and the water level electrode 1020b output a detection signal to the controller 1200 when they are in contact with water. Based on detection signals from the water level electrodes 1020a and 1020b, the controller 1200 determines whether the water level of the cistern 1020 exceeds the high level water level, between the high level water level and the low level water level, or lower than the low level water level. To do. The water level in the cis turn 1020 is in a proper state when it is located within the range between the high level and the low level. The controller 1200 controls the opening and closing of the makeup water valve 1022 based on the detection signals from the water level electrodes 1020a and 1020b, and maintains the water level of the cistern 1020 within an appropriate range.

  One end of a cis-turn forward path 1024 is connected to the bottom of the cis-turn 1020. A pump 1026 is provided in the cistern forward path 1024. The pump 1026 is controlled by the controller 1200. The other end of the systern outbound path 1024 branches into a low temperature heating outbound path 1028 and a first warm water path 1030.

  The low-temperature heating forward path 1028 branched from the cistern outward path 1024 is connected to the inlet of the low-temperature heating machine 1032. The low temperature heater 1032 of the present embodiment is a floor heater. A thermal valve 1034 is inserted in the low temperature heating forward path 1028. The thermal valve 1034 is controlled by the controller 1200. The thermal valve 1034 is opened when the low temperature heater 1032 is used. While the low temperature heater 1032 is not used, the thermal valve 1034 is closed. One end of a low-temperature heating return path 1036 is connected to the outlet of the low-temperature heater 1032. The other end of the low temperature heating return path 1036 is connected to the first cold water path 1038.

  The first cold water passage 1038 is connected to the inlet of the cooler cooling unit 130. One end of the second cold water passage 1040 is connected to the outlet of the cooler cooling unit 130. The other end of the second cold water passage 1040 is connected to the inlet of the first latent heat exchanger 150 of the first combustion device 1006. One end of the third cold water channel 1042 is connected to the outlet of the first latent heat exchanger 150. The other end of the third cold water passage 1042 is connected to the inlet of the second latent heat exchanger 180 of the second combustion device 1044.

  The second combustion device 1044 includes a second burner 160, a second sensible heat exchanger 170, a second latent heat exchanger 180, and a blower fan 1052. The combustion gas obtained by the second burner 160 is blown out by the blower fan 1052, and after heating the water flowing inside the second sensible heat exchanger 170 and the water flowing inside the second latent heat exchanger 180, , Discharged outside. The second sensible heat exchanger 170 is a heat transfer tube passing through the inside of the second combustion device 1044, and performs heat exchange between water passing through the heat transfer tube and combustion gas flowing outside the heat transfer tube. The second latent heat exchanger 180 is a heat transfer tube that passes through the inside of the second combustion device 1044, and performs heat exchange between water that passes through the inside of the heat transfer tube and combustion gas that flows outside the heat transfer tube. Since low temperature water passes through the inside of the second latent heat exchanger 180, water vapor contained in the combustion gas flowing outside condenses on the surface of the second latent heat exchanger 180. The water flowing in the second latent heat exchanger 180 is heated by the condensation heat of the water vapor at this time.

  The outlet of the second latent heat exchanger 180 is connected to one end of the systern return path 1054. The other end of the cistern return path 1054 is connected to the bottom of the cistern 1020.

A first hot water passage 1030 branched from the cistern outward passage 1024 is connected to the inlet of the first sensible heat exchanger 140 of the first combustion device 1006. One end of the second hot water passage 1056 is connected to the outlet of the first sensible heat exchanger 140. The other end of the second hot water passage 1056 is connected to the inlet of the second sensible heat exchanger 170 of the second combustion device 1044. One end of a third hot water passage 1058 is connected to the outlet of the second sensible heat exchanger 170. The third hot water passage 1058 is branched into a thermal valve passage 1062, a high temperature heating forward passage 1064, a hot water supply heating forward passage 1066, and a bath hot water supply heating forward passage 1068.
The first hot water channel 1030 is provided with a thermistor 1092 to detect the temperature of water flowing through the first hot water channel, that is, the temperature of hot water pumped from the cistern 1020. The third hot water channel 1058 is provided with a thermistor 1060 to detect the temperature of water flowing through the third hot water channel 1058. The thermistors 1060 and 1092 output the detected water temperature to the controller 1200.

  A thermal valve passage 1062 branched from the third hot water passage 1058 is connected to a systern return passage 1054. A thermal valve 1070 is inserted in the thermal valve path 1062. The thermal valve 1070 is controlled by the controller 1200. The thermal valve path 1062 is provided with a bypass path 1072 that bypasses the thermal valve 1070.

  The high temperature heating forward path 1064 branched from the third hot water path 1058 is connected to the inlet of the high temperature heating machine 1074. The high temperature heater 1074 of the present embodiment is a bathroom heater. The high temperature heater 1074 includes a thermal valve 1074a. The thermal valve 1074a is controlled by the controller 1200. When the high temperature heater 1074 is used, the thermal valve 1074a is opened. While the high temperature heater 1074 is not used, the thermal valve 1074a is closed. One end of a high temperature heating return path 1076 is connected to the outlet of the high temperature heater 1074. The other end of the high temperature heating return path 1076 is connected to the return path 1078. The return path 1078 is connected to the first cold water path 1038.

  A hot-water supply heating forward path 1066 branched from the third hot water path 1058 is connected to an inlet of the first flow path 1080a of the heat exchanger 1080. The heat exchanger 1080 includes a first flow path 1080a and a second flow path 1080b therein, and exchanges heat between the fluid passing through the first flow path 1080a and the fluid passing through the second flow path 1080b. Do. A thermal valve 1082 is inserted in the hot water supply heating forward path 1066. One end of a hot water supply heating return path 1084 is connected to the outlet of the first flow path 1080a of the heat exchanger 1080. The other end of the hot water heating return path 1084 is connected to the return path 1078.

  The bath hot water heating forward path 1068 branched from the third hot water path 1058 is connected to the inlet of the first flow path 1086a of the heat exchanger 1086. The heat exchanger 1086 includes a first flow path 1086a and a second flow path 1086b therein, and performs heat exchange between a fluid passing through the first flow path 1086a and a fluid passing through the second flow path 1086b. . A thermal valve 1088 is provided in the bath hot water heating forward path 1068. One end of a bath hot water heating return path 1090 is connected to the outlet of the first flow path 1086a of the heat exchanger 1086. The other end of the bath hot water heating return path 1090 is connected to the return path 1078.

The water heater 1100 includes a third combustion device 1102 and a heat exchanger 1080. A tap water path 1104 having one end connected to the water supply is connected to the inlet of the third latent heat exchanger 1106 of the third combustion apparatus 1102.
The third combustion device 1102 includes a third burner 1108, a third sensible heat exchanger 1110, a third latent heat exchanger 1106, and a blower fan 1112. The combustion gas obtained by the third burner 1108 was blown out by the blowing fan 1112 to heat the water flowing inside the third sensible heat exchanger 1110 and the water flowing inside the third latent heat exchanger 1106. Later, it is discharged to the outside. The third sensible heat exchanger 1110 is a heat transfer tube passing through the inside of the third combustion device 1102, and performs heat exchange between water passing through the inside of the heat transfer tube and combustion gas flowing outside the heat transfer tube. The third latent heat exchanger 1106 is a heat transfer tube that passes through the inside of the third combustion device 1102, and performs heat exchange between water that passes through the inside of the heat transfer tube and combustion gas that flows outside the heat transfer tube. Since low-temperature water passes through the inside of the third latent heat exchanger 1106, water vapor contained in the combustion gas flowing outside condenses on the surface of the third latent heat exchanger 1106. The water flowing in the third latent heat exchanger 1106 is heated by the condensation heat of the water vapor at this time.

  One end of the first hot water supply passage 1114 is connected to the outlet of the third latent heat exchanger 1106. The other end of the first hot water supply path 1114 is connected to the inlet of the second flow path 1080b of the heat exchanger 1080. One end of the second hot water supply path 1116 is connected to the outlet of the second flow path 1080b of the heat exchanger 1080. The other end of the second hot water supply passage 1116 is connected to the inlet of the third sensible heat exchanger 1110 of the third combustion device 1102. One end of a third hot water supply passage 1118 is connected to the outlet of the third sensible heat exchanger 1110. The other end of the third hot water supply passage 1118 is connected to the hot water tap 1120. The hot water tap 1120 is disposed in a bathroom, a washroom, a kitchen, or the like. In FIG. 1, these hot water taps are represented by one hot water tap 1120.

  The tap water path 1104 is provided with a thermistor 1122 and a flow sensor 1128. A thermistor 1124 is provided in the second hot water supply passage 1116. A thermistor 1126 is provided in the third hot water supply passage 1118. The thermistors 1122, 1124, and 1126 are sensors that detect the water temperature, and output the detected water temperature to the controller 1200. The flow sensor 1128 is a sensor that detects the amount of water, and outputs the detected amount of water to the controller 1200.

  The bath water heater 1130 includes a heat exchanger 1086. One end of a bathtub outward path 1134 is connected to the suction port 1132a of the bath tub 1132. A pump 1136 is provided in the bathtub outward path 1134. The pump 1136 is controlled by the controller 1200. The other end of the bathtub forward path 1134 is connected to the inlet of the second flow path 1086b of the heat exchanger 1086. One end of the bathtub return path 1138 is connected to the outlet of the second flow path 1086b of the heat exchanger 1086. The other end of the bathtub return path 1138 is connected to the supply port 1132 b of the bathtub 1132. A water flow switch 1140 and a thermistor 1142 are provided in the bathtub forward path 1134. A water level sensor 1144 is provided in the bathtub return path 1138. The water flow switch 1140, the thermistor 1142, and the water level sensor 1144 output detection signals to the controller 1200. The water level sensor 1144 detects the water pressure. The controller 1200 estimates the water level of hot water stretched on the bathtub 1132 from the water pressure detected by the water level sensor 1144. The water flow switch 1140 is turned on when water flows through the bathtub outward path 1134. The thermistor 1142 detects the temperature of the hot water sucked from the bathtub 1132.

The third hot water supply path 1118 of the water heater 1100 and the bathtub return path 1138 of the bath water heater 1130 are connected via a hot water supply path 1146. The pouring passage 1146 is provided with a solenoid drive type pouring valve 1148. The pouring valve 1148 is controlled by the controller 1200. When hot water is filled in the bathtub 1132, the pouring valve 1148 is opened. When the pouring valve 1148 is opened, hot water flows from the third hot water supply passage 1118 into the pouring passage 1146, and the hot water that has flowed into the pouring passage 1146 flows into the bathtub return passage 1138. Hot water that has flowed into the bathtub return path 1138 is supplied to the bathtub 1132 from the suction port 1132a and the supply port 1132b. Thereby, hot water is filled in the bathtub 1132.
A flow rate sensor 1150 is provided in the pouring channel 1146. The flow sensor 1150 outputs a detection signal to the controller 1200. The controller 1200 estimates the amount of hot water filling the bathtub 1132 from the flow rate detected by the flow rate sensor 1150.

  A replenishment water channel 1152 branches from the third hot water channel 1118 of the water heater 1100. The make-up water channel 1152 supplies water from the third hot water supply channel 1118 to the upper part of the cistern 1020. A makeup water valve 1022 is inserted in the makeup water channel 1152.

  The electric power generated by the generator 116 is supplied to the grid box 1010. The grid box 1010 supplies the power supplied from the generator 116 to the household power supply. The grid box 1010 can communicate with the controller. The grid box 1010 measures the frequency of the power supplied from the generator 116 and outputs it to the controller 1200. If the frequency of the measured power is significantly different from the frequency of the home power supply, the controller 1200 instructs the grid box 1010 to supply the power to the heater 1154 without supplying the power to the home power supply. . The heater 1154 heats the hot water that passes through the second hot water passage 1056. When the frequency of the measured power is substantially the same as the frequency of the household power supply, the controller 1200 instructs the grid box 1010 to supply the power to the household power supply.

  The remote controller 1202 is disposed in the bathroom. The remote controller 1202 can communicate with the controller 1200. The user can set a desired hot water supply temperature, a hot water temperature of the bath, and a hot water filling amount by operating the remote controller 1202. Information input to the remote controller 1202 is output to the controller 1200. The controller 1200 controls the entire cogeneration system 1000 by operating the remote controller 1202 or by a signal from a sensor such as the water level sensor 1144, such as a thermal valve or the water level of the cistern 1020. Note that description of the control of the cogeneration system 1000 is omitted.

In the cogeneration system 1000 of the present embodiment, the water cooled to low temperature by the low temperature heater 1032 or the high temperature heater 1074 or the hot water supply heating is supplied to the cooler cooling unit 130 of the power generation apparatus 1002 without heating. Yes. As a result, the temperature of the working fluid passing through the cooler (not shown) of the Stirling engine 110 can be greatly reduced, and the electric power generated by the generator 116 can be increased.
In the present embodiment, the temperature of the water is also raised by the heat recovered from the cooler cooling unit 130 that cools the cooler unit of the Stirling engine 110. Liquid using not only the thermal energy of the combustion gas generated by the first burner for heating the heater unit 112 of the Stirling engine 110 but also the thermal energy recovered from the cooler cooling unit 130 for cooling the cooler unit of the Stirling engine 110. (Water) is heated. The heat energy generated when the Stirling engine is driven can be efficiently recovered and supplied to the outside.
Further, in this embodiment, the second heat consuming device 310b shown in FIG. 2 includes a high-temperature heater 1074, a hot water heater 1100, and a bath water heater 1130. Hot water can be supplied to the plurality of second heat consuming devices 310b.
In addition, as described in the embodiment, the cogeneration system 1000 of the present example has a second liquid flow path for the high temperature heater 1074, the hot water heater 1100, and the bath water heater 1130 that require high temperature water. It is possible to supply water having a high temperature after passing through the first sensible heat exchanger 140 and the second sensible heat exchanger 170 connected in the middle. On the other hand, the low-temperature heater 1032 which is a floor heater operates sufficiently at a temperature lower than the temperature required for the high-temperature heater 1074 or the like. For such a low temperature heater 1032, a high temperature heater 1074 is provided by a cooler cooling unit 130, a first latent heat exchanger 150, and a second latent heat exchanger 180 connected in the middle of the first liquid flow path 200. Although the temperature is not high enough to be suitable for the low temperature heater 1032, hot water having an appropriate temperature can be supplied. That is, the cogeneration system 1000 of the present embodiment can supply hot water having two types of temperatures, and can simultaneously supply water having temperatures suitable for the respective heating devices.

In this embodiment, the cooler cooling unit 130, the first latent heat exchanger 150, and the second latent heat exchanger 170 are passed by the first hot water passage 1030 corresponding to the third liquid passage 280 shown in FIG. A part of the water is supplied to the second liquid channel 250.
In addition, a part of the water that has passed through the first sensible heat exchanger 140 and the second sensible heat exchanger 170 by the second liquid flow path 250 and has reached a high temperature passes through the thermal valve path 1062 and the bypass path 1072. To the systern return path 1054 constituting a part of the first liquid flow path 200.
That is, in this embodiment, the water that has passed through the first liquid channel 200 and the liquid that has passed through the second liquid channel 250 are mixed in the cistern 1020. Then, the liquid mixed in the cistern 1020 is divided into the first liquid channel 200 and the second liquid channel 250.
With this configuration, the temperature of water supplied to the low-temperature heater 1032 (corresponding to the first heat consuming device), the high-temperature heater 1074, the water heater 1100, and the bath water heater 1130 (these correspond to the second heat consuming device). ) Can be adjusted by the first sensible heat exchanger 140, the first latent heat exchanger 150, the second sensible heat exchanger 170, and the second latent heat exchanger 180.
In the present embodiment, the first sensible heat exchanger 140 and the first latent heat using the thermal energy of the first combustion gas obtained by the first burner 120 for the first purpose of heating the heater portion 112 of the Stirling engine 110 are used. The heat energy of the second combustion gas obtained by the second burner 160 capable of adjusting the amount of heat energy (combustion gas temperature or amount) of the combustion gas independently of the heat exchanger 150 and the first burner 120 is used. By providing the second sensible heat exchanger 170 and the second latent heat exchanger 180, cogeneration that efficiently uses the sensible heat and latent heat energy of the combustion gas obtained by the first burner 120 and the second burner 160. An apparatus can be realized. Furthermore, the thermal energy of the combustion gas obtained by the first burner 120 and the second burner 160 is efficiently used, and the appropriate temperature for each of the first heat consuming device and the second heat consuming device having different required water temperatures. Of water can be supplied.

Specific examples of the present invention have been described in detail above, but these are merely examples and do not limit the scope of the claims. The technology described in the claims includes various modifications and changes of the specific examples illustrated above.
For example, in the first embodiment, the first liquid flow path is configured so that the liquid flows through the cooler cooling unit 130 prior to the first latent heat exchanger 150 and the second latent heat exchanger 180. In contrast, the first liquid flow path may be configured such that the liquid flows through the cooler cooling unit 130 after passing through the first latent heat exchanger 150 and the second latent heat exchanger 180. By doing so, the water having a low temperature due to the heating in the low temperature heater 1032 or the high temperature heater 1074 or the hot water supply heating is supplied to the first latent heat exchanger 150 and the second latent heat exchanger 180 without heating. is doing. Thus, water vapor contained in the combustion gas of the first combustion device 1006 and the second combustion device 1044 can be reliably condensed, and latent heat can be reliably recovered from the combustion gas. The heat utilization efficiency of the entire system is improved.
The technical elements described in this specification or the drawings exhibit technical usefulness alone or in various combinations, and are not limited to the combinations described in the claims at the time of filing. Moreover, the technique illustrated in this specification or the drawings achieves a plurality of objects at the same time, and has technical usefulness by achieving one of the objects.

It is a mimetic diagram of a cogeneration system of one embodiment of the present invention. It is a schematic diagram of the cogeneration system of other embodiment of this invention. It is a schematic diagram of the cogeneration system of the Example of this invention.

Explanation of symbols

100a, 100b, 1000: cogeneration system 110: Stirling engine 112: heater unit 114: cooler unit 116: generator 118: displacer 120: first burner 122: first combustion gas flow path 130: cooler cooling unit 140: first Sensible heat exchanger 150: first latent heat exchanger 160: second burner 170: second sensible heat exchanger 180: second latent heat exchanger 200: first liquid flow path 202: first liquid inlet 204 : First liquid outlet 250: second liquid channel 254: second liquid outlet 274: second liquid inlet 278: fourth liquid channel 280: third liquid channel 300: first heat consuming device 310, 310b: second heat consuming device 1006: first combustion device 1010: grid box 1020: cis turn 1024: cis turn outward 1026: pump 102 : Low temperature heating forward path 1030: first hot water path 1032: low temperature heater 1036: low temperature heating return path 1038: first cold water path 1040: second cold water path 1042: third cold water path 1044: second combustion device 1054: systern return path 1056: Second hot water path 1058: Third hot water path 1064: High temperature heating forward path 1066: Hot water heating heating forward path 1068: Bath hot water heating heating forward path 1072: Bypass path 1074: High temperature heater 1076: High temperature heating return path 1078: Return path 1080: Heat exchanger 1084 : Hot water heating return path 1086: heat exchanger 1090: bath hot water heating return path 1100: hot water heater 1102: third combustion device 1104: tap water path 1106: third latent heat exchanger 1108: third burner 1110: third sensible heat Exchanger 1114: First hot water supply path 1116: Second hot water supply path 1118: Third hot water supply path 1120: Hot water tap 130: Bath water heater 1132: bathtub 1134: Tub forward 1136: Pump 1138: Tub Return 1152: Supply waterways 1154: heater 1200: controller 1202: Remote Control

Claims (6)

A cogeneration system that supplies power and heat,
A Stirling engine having a heater and a cooler for reciprocating the displacer and the piston, together with a generator connected,
A first burner for heating the heater part of the Stirling engine;
A first sensible heat exchanger that is disposed upstream of the flow path of the first combustion gas generated by the combustion of the first burner and raises the temperature of the liquid by the heat of the first combustion gas;
A first latent heat exchanger that is disposed downstream of the flow path of the first combustion gas and that heats the liquid by the condensation heat of water vapor in the first combustion gas that has passed through the first sensible heat exchanger;
The second burner,
A second sensible heat exchanger that is disposed upstream of the flow path of the second combustion gas generated by the combustion of the second burner and raises the temperature of the liquid by the heat of the second combustion gas;
A second latent heat exchanger that is disposed on the downstream side of the second combustion gas flow path and that raises the temperature of the liquid by the condensation heat of water vapor in the second combustion gas that has passed through the second sensible heat exchanger;
A cooler cooling section for passing a liquid that cools the cooler section of the Stirling engine;
The liquid inflow port can be connected to the liquid discharge port of the first heat consuming device, the liquid outflow port can be connected to the liquid supply port of the first heat consuming device, and the liquid flowing in from the liquid inflow port can be connected to the first latent heat. A first liquid flow path that passes through the heat exchanger, the second latent heat exchanger, the cooler cooling section, and then leads to the liquid outlet;
The liquid is supplied from one end, the other end can be connected to the liquid supply port of the second heat consuming device, and the supplied liquid passes through the first sensible heat exchanger and the second sensible heat exchanger. A second liquid flow path that leads to the other end connectable to the liquid supply port of the second heat consuming device,
Cogeneration system characterized by comprising.   The first liquid channel is connected to a first heat consuming device operable with a liquid having a temperature lower than that of the second heat consuming device to which the liquid flowing through the second liquid channel is supplied. The cogeneration system according to 1.   The first liquid flow path is arranged so that the liquid flowing in from the liquid inlet passes through the cooler cooling section before the first latent heat exchanger and the second latent heat exchanger. The cogeneration system according to claim 1 or 2.   The first liquid channel is arranged such that the liquid flowing in from the liquid inlet passes through the cooler cooling unit after passing through the first latent heat exchanger and the second latent heat exchanger. The cogeneration system according to claim 1 or 2.   One end is branched from the first liquid channel at a portion closer to the liquid outlet than the first latent heat exchanger, the second latent heat exchanger, and the cooler cooling unit, and the other end is an end of the second liquid channel. The cogeneration system according to any one of claims 1 to 4, further comprising a third liquid flow path communicating with an end portion on a liquid supply side.   One end can be connected to the liquid discharge port of the second heat consuming device, and the other end is connected to the first latent heat heat exchanger, the second latent heat heat exchanger, and the cooler cooling portion closer to the liquid inlet. The cogeneration system according to any one of claims 1 to 5, further comprising a fourth liquid flow path communicating with the path.

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