JP4605597B2 - Cogeneration system - Google Patents

Description

  The present invention relates to a cogeneration system that performs cogeneration, and more particularly to a cogeneration system that is configured so that exhaust heat can be used efficiently.

  In conventional cogeneration systems, control is performed based on the concept that there is sufficient exhaust heat.

  However, in recent years, power generation efficiency has been improved, and the amount of exhaust heat is decreasing compared to the conventional one. In addition, the amount of exhaust heat utilization has been increasing due to the improvement in the performance of exhaust heat utilization equipment. As described above, when the power generation efficiency and the performance of the exhaust heat utilization device are improved, a phenomenon in which the amount of exhaust heat is insufficient is predicted in reverse to the conventional case, and control of a different concept from before is required.

  With reference to FIG. 23, the control in exhaust heat utilization in the conventional cogeneration system will be described.

  The conventional cogeneration system of FIG. 23 includes a prime mover 10, a waste heat recovery heat exchanger 20, a cooling tower 30, a first waste heat utilization device 40 having a waste heat utilization heat exchanger 41, and waste heat utilization. A second exhaust heat utilization device 50 having a heat exchanger 51, and the prime mover 10, the exhaust heat recovery heat exchanger 20 and the cooling tower 30 communicate with each other so as to be circulated by the primary side circulation line L100, The exhaust heat recovery heat exchanger 20, the first exhaust heat utilization device 40, and the second exhaust heat utilization device 50 communicate with each other so as to be circulated by the secondary side circulation line L <b> 200.

The primary side circulation line L100 includes a pipe L111 connecting the prime mover 10 and the exhaust heat recovery heat exchanger 20, a pipe L112 connecting the exhaust heat recovery heat exchanger 20 and the branch point b1, and a branch point b1 and three. a pipe L 113 which connects the square valve V, a pipe L114 connecting the branch point b1 and the cooling tower 30, a pipe L115 connecting the cooling tower 30 and a three-way valve V, three-way valve V and the prime mover 10 And a pipe L116 for connecting the two.

  The secondary side circulation line (exhaust heat hot water line) L200 includes a pipe L201 connecting the exhaust heat recovery heat exchanger 20 and the first branch point b21, the first branch point b21 and the first exhaust heat utilization device. A pipe L202 connecting the second branch point b22 on the 40 side, a pipe L203 connecting the second branch point b22 and the three-way valve V1 on the first exhaust heat utilization device 40 side, and a second branch point piping L204 which connects b22 and the waste heat utilization heat exchanger 41 by the side of the 1st waste heat utilization apparatus 40, waste heat utilization heat exchanger 41 by the side of the 1st waste heat utilization apparatus 40, and 1st waste heat A pipe L205 that connects the three-way valve V1 on the use device 40 side and a pipe L206 that connects the three-way valve V1 on the first exhaust heat use device 40 side and the fourth junction point g are included.

Furthermore, the secondary circulation line L200 includes a pipe L 207 that connects the first branch point b21 and second branch point of the second exhaust heat utilizing device 50 side b23, a third branch point b23 A pipe L208 that connects the three-way valve V2 on the second waste heat utilization device 50 side, and a pipe that connects the third branch point b23 and the waste heat utilization heat exchanger 51 on the second waste heat utilization device 50 side. L 209 , a pipe L 210 connecting the exhaust heat utilization heat exchanger 51 on the second exhaust heat utilization device 50 side and the three-way valve V2 on the second exhaust heat utilization device 50 side, and the second exhaust heat utilization A pipe L 211 that connects the three-way valve V2 on the device 50 side and the junction point g and a pipe L 212 that connects the junction point g and the exhaust heat recovery heat exchanger 20 are provided.

  The pipe L211 is provided with a pump 70 that pumps exhaust hot water circulating through the secondary circulation line L200.

  In the primary side circulation line L100, the high-temperature cooling water discharged from the prime mover 10 exchanges heat with the waste heat hot water circulating in the secondary side circulation line 200 in the waste heat recovery heat exchanger 20 (to the waste heat hot water). When the cooled cooling water is sufficiently cooled, it is returned to the prime mover 10 via the pipes L112, L113, and L116 without passing through the cooling tower 30.

  On the other hand, when the cooled cooling water does not fall sufficiently, it passes through the cooling tower 30, that is, through the pipe L112, the branch point b1, the pipe L114, the cooling tower 30, the pipe L115, the three-way valve V, and the pipe L116. Then, it is returned to the prime mover 10.

In the secondary side circulation line L200 (exhaust heat hot water line), exhaust heat hot water that has received high-temperature exhaust heat energy from the primary circulation line in the exhaust heat recovery heat exchanger 20 is pipe L201, branch point b21, pipe L202, Via the branch point b22 and the pipe L204, to the exhaust heat utilization heat exchanger 41 (third heat medium not shown) of the first exhaust heat utilization apparatus 40, and to the branch point b21, the pipe L207, and the branch point b23. Then, the waste heat utilization heat exchanger 51 of the second waste heat utilization device 50 (a tertiary heat medium (not shown)) of the second waste heat utilization device 50 is supplied via the pipe L209.
In the exhaust heat utilization heat exchanger 41 of the first exhaust heat utilization device 40 and the exhaust heat utilization heat exchanger 51 of the second exhaust heat utilization device 50, the temperature is lowered by exchanging heat with a tertiary heat medium (not shown). The waste heat hot water joins at the junction point g via the pipe L205, the three-way valve V1, the pipe L206, and the pipe L210, the three-way valve V2, and the pipe L211, respectively, and the waste heat recovery heat exchanger 20 passes through the pipe L212. Returned to

Here, in the first exhaust heat utilizing device 40 side has a temperature sensor T ta provided in the region of the pipe L202 (inlet side of the exhaust heat utilizing device 40), the heat from the exhaust heat utilizing device 40 to the waste heat hot water In order to prevent backflow, when the exhaust heat hot water to the exhaust heat utilization heat exchanger 41 is lower than a predetermined temperature, the exhaust heat utilization heat exchange is performed when the temperature exceeds the predetermined temperature. The three-way valve V1 is ON / OFF controlled so as to switch to the container 41 side.

On the other hand, on the second exhaust heat utilization device 50 side, a temperature sensor T tb is provided in the region of the pipe L211 (exit side of the exhaust heat utilization device 50), and in order to prevent a decrease in the exhaust heat hot water temperature, the exhaust heat utilization device When the exhaust heat hot water temperature from 50 falls below a predetermined value, when it exceeds the bypass pipe side, that is, the pipe L208 side, when the exhaust heat hot water temperature rises, a partial intermediate opening is set so as to switch to the exhaust heat utilization heat exchanger 51 side. Including ON-OFF control.

However, in the control on the first exhaust heat utilization device 40 side, when the amount of exhaust heat from the prime mover 10 or the like falls below the exhaust heat utilization fee, the three-way valve V1 is caused by a decrease in the temperature of the exhaust heat hot water flowing through the secondary side L200. Repeated opening and closing causes the following problems.
(A) The output of the exhaust heat utilization device 40 becomes unstable and adversely affects, for example, the control of the number of air conditioners (for example, the operation and stop of a backup boiler, etc. are repeated).
(B) The temperature of the wastewater warm water becomes unstable, transiently dissipates heat from the cooling tower 30 of the primary side L100, and the exhaust heat utilization rate deteriorates. That is, in the middle of the control, the heat is temporarily discarded via the cooling tower 30, and the exhaust heat is not effectively used.
If the exhaust heat is used excessively (the secondary side L200 has a larger amount of circulating water), the three-way valves V1 and V2 operate so as to flow on the bypass side, and a state where they are not effectively used during the transition period will occur. .

  In the control on the second exhaust heat utilization device 50 side, controlling with the exhaust heat hot water outlet temperature from the exhaust heat utilization device 50 means that the exhaust heat utilization amount per exhaust heat utilization device is limited. Therefore, if some of the exhaust heat utilization devices are stopped, the available exhaust heat amount of the operating exhaust heat utilization devices will increase, but the exhaust heat utilization amount is limited, so the entire system Exhaust heat utilization rate of will deteriorate.

  When exhaust heat usage is restricted, if not all of the exhaust heat utilization equipment is stopped but only a part of it is stopped, the remaining exhaust heat utilization equipment in operation is used for all exhaust heat utilization equipment. It is possible to input a larger amount of exhaust heat than the amount of exhaust heat that can be input per unit when the device is input. However, since the amount of exhaust heat utilization is limited, in such cases (only a part of the exhaust heat utilization equipment is stopped, and the exhaust heat utilization equipment for each remaining exhaust heat utilization equipment in operation Even when all of the exhaust heat utilization devices are operating, only the amount of exhaust heat is input.

As another conventional technology, the exhaust heat recovery heat source device that generates cold / hot water using exhaust heat as a drive source and a bypass pipe have a flow rate of the cold / hot water pump on the cooling / heating load side based on the state of the exhaust heat. There exists a technique for controlling (see Patent Document 1).
However, this technology does not solve the problems described above, that is, the output of the exhaust heat utilization device and the exhaust heat hot water temperature become unstable, or the exhaust heat utilization efficiency of the entire system decreases. .
JP 2002-162087 A

  The present invention has been proposed in view of the above-mentioned problems of the prior art, and can eliminate the instability of the output of the exhaust heat utilization device and the exhaust heat hot water temperature. The purpose is to provide a cogeneration system that can prevent the waste heat utilization efficiency from decreasing.

  According to the present invention, the prime mover (1), the exhaust heat recovery heat exchanger (2), and the cooling tower (3) form a circulation channel by the primary side hot water line (L1), and the primary side hot water line (L1) includes a flow path (L13) that bypasses the cooling tower (3), and the exhaust heat recovery heat exchanger (2) and a plurality of exhaust heat utilization devices (4, 5) are connected to the secondary hot water line. (L2) forms a circulation flow path, and the secondary hot water line (L2) includes flow paths (L221, L231) that bypass the plurality of waste heat utilization devices (4, 5), and the secondary side In the cogeneration system in which the bypass flow path (L221, L231) of the hot water line (L2) and the outlet side of the exhaust heat utilization device (4, 5) merge and return to the exhaust heat recovery heat exchanger (2) , Each of the plurality of exhaust heat utilization devices (4, 5) has a secondary hot water line. There are provided hot water supply amount determining devices (Vf1 to Vf3) for determining the supply amount of the hot water flowing through (L2) to the plurality of exhaust heat utilization devices (4, 5), and the exhaust heat utilization devices (4, 5). ) Is provided with measuring devices (St1 to St3) for measuring hot water inlet temperatures to the plurality of exhaust heat utilization devices (4, 5), and the plurality of exhaust heat utilization devices (4). 5) having a control device (8) configured to proportionally control the amount of hot water supplied to the plurality of exhaust heat utilization devices (4, 5) corresponding to the temperature of the hot water near the upstream side of 5) ing.

  According to the present invention, the prime mover (1), the exhaust heat recovery heat exchanger (2), and the cooling tower (3) form a circulation channel by the primary side hot water line (L1), and the primary side hot water line (L1) includes a flow path (L13) that bypasses the cooling tower (3), and the exhaust heat recovery heat exchanger (2) and a plurality of exhaust heat utilization devices (4, 5) are connected to the secondary hot water line. (L2) forms a circulation flow path, and the secondary hot water line (L2) includes flow paths (L221, L231) that bypass the plurality of waste heat utilization devices (4, 5), and the secondary side In the cogeneration system in which the bypass flow path (L221, L231) of the hot water line (L2) and the outlet side of the exhaust heat utilization device (4, 5) merge and return to the exhaust heat recovery heat exchanger (2) , Each of the plurality of exhaust heat utilization devices (4, 5) has a secondary hot water line. A hot water supply amount determination device (Vf1 to Vf3) for determining the supply amount of the hot water flowing through (L2) to the plurality of exhaust heat utilization devices (4, 5) is provided, and the secondary side hot water line (L2) An exhaust heat recovery heat exchanger (2) outlet temperature measuring device (St22) is provided and exhaust heat corresponding to the exhaust heat recovery heat exchanger (2) outlet temperature of the secondary hot water line (L2). It has a control device (8) configured to proportionally control the amount of hot water supplied to the utilization device (4, 5).

  According to the present invention, the prime mover (1), the exhaust heat recovery heat exchanger (2), and the cooling tower (3) form a circulation channel by the primary side hot water line (L1), and the primary side hot water line (L1) includes a flow path (L13) that bypasses the cooling tower (3), and the exhaust heat recovery heat exchanger (2) and a plurality of exhaust heat utilization devices (4, 5) are connected to the secondary hot water line. (L2) forms a circulation flow path, and the secondary hot water line (L2) includes flow paths (L221, L231) that bypass the plurality of waste heat utilization devices (4, 5), and the secondary side In the cogeneration system in which the bypass flow path (L221, L231) of the hot water line (L2) and the outlet side of the exhaust heat utilization device (4, 5) merge and return to the exhaust heat recovery heat exchanger (2) , Each of the plurality of exhaust heat utilization devices (4, 5) has a secondary hot water line. A hot water supply amount determination device (for example, three-way valves Vf1 to Vf3) for determining the supply amount to the exhaust heat utilization equipment (4, 5) flowing through (L2) is provided, and the secondary side hot water line (L2) ) Exhaust heat recovery heat exchanger (2) Inlet temperature measuring device (temperature sensor St33) is provided and the exhaust heat recovery heat exchanger (2) inlet temperature (temperature) of the secondary hot water line (L2) A control device (control unit) configured to proportionally control the amount of hot water supplied to the exhaust heat utilization device (4, 5) corresponding to the hot water temperature measured by the sensor St33: secondary side hot water inlet temperature) 8).

  According to the present invention, the prime mover (1), the exhaust heat recovery heat exchanger (2), and the cooling tower (3) form a circulation channel by the primary side hot water line (L1), and the primary side hot water line (L1) includes a flow path (L13) that bypasses the cooling tower (3), and the exhaust heat recovery heat exchanger (2) and a plurality of exhaust heat utilization devices (4, 5) are connected to the secondary hot water line. (L2) forms a circulation flow path, and the secondary hot water line (L2) includes flow paths (L221, L231) that bypass the plurality of waste heat utilization devices (4, 5), and the secondary side In the cogeneration system in which the bypass flow path (L221, L231) of the hot water line (L2) and the outlet side of the exhaust heat utilization device (4, 5) merge and return to the exhaust heat recovery heat exchanger (2) , Each of the plurality of exhaust heat utilization devices (4, 5) has a secondary hot water line. A hot water supply amount determining device (for example, three-way valves Vf1 to Vf3) for determining the supply amount of the hot water flowing through (L2) to the exhaust heat utilization equipment (4, 5) is provided, and the primary side hot water line (L1) ) Exhaust heat recovery heat exchanger (2) An outlet temperature measuring device (temperature sensor St5) is provided, and the exhaust heat recovery heat exchanger outlet temperature (temperature sensor St5) of the primary hot water line is measured. A control device (control unit 8) configured to proportionally control the amount of hot water supplied to the exhaust heat utilization device (4, 5) corresponding to the hot water temperature (primary hot water outlet temperature). Yes.

  According to the present invention, the prime mover (1), the exhaust heat recovery heat exchanger (2), and the cooling tower (3) form a circulation channel by the primary side hot water line (L1), and the primary side hot water line (L1) includes a flow path (L13) that bypasses the cooling tower (3), and the exhaust heat recovery heat exchanger (2) and a plurality of exhaust heat utilization devices (4, 5) are connected to the secondary hot water line. (L2) forms a circulation flow path, and the secondary hot water line (L2) includes flow paths (L221, L231) that bypass the plurality of waste heat utilization devices (4, 5), and the secondary side In the cogeneration system in which the bypass flow path (L221, L231) of the hot water line (L2) and the outlet side of the exhaust heat utilization device (4, 5) merge and return to the exhaust heat recovery heat exchanger (2) , Each of the plurality of waste heat utilization devices (4, 5) has a secondary hot water line. A hot water supply amount determining device (for example, three-way valves Vf1 to Vf3) for determining the supply amount of the hot water flowing through (L2) to the exhaust heat utilization equipment (4, 5) is provided, and the primary hot water line (L1 ) Exhaust heat recovery heat exchanger (2) Inlet temperature measurement device (temperature sensor St4) is provided and the exhaust heat recovery heat exchanger (2) inlet temperature (temperature) of the primary hot water line (L1) A control device (control unit) configured to proportionally control the amount of hot water supplied to the exhaust heat utilization device (4, 5) corresponding to the hot water temperature measured by the sensor St4: primary hot water inlet temperature) 8).

  According to the present invention, the prime mover (1), the exhaust heat recovery heat exchanger (2), and the cooling tower (3) form a circulation channel by the primary side hot water line (L1), and the primary side hot water line (L1) includes a flow path (L13) that bypasses the cooling tower (3), and the exhaust heat recovery heat exchanger (2) and a plurality of exhaust heat utilization devices (4, 5) are connected to the secondary hot water line. (L2) forms a circulation flow path, and the secondary hot water line (L2) includes flow paths (L221, L231) that bypass the plurality of waste heat utilization devices (4, 5), and the secondary side In the cogeneration system in which the bypass flow path (L221, L231) of the hot water line (L2) and the outlet side of the exhaust heat utilization device (4, 5) merge and return to the exhaust heat recovery heat exchanger (2) , Each of the plurality of exhaust heat utilization devices (4, 5) has a secondary hot water line. A hot water supply amount determination device (for example, three-way valves Vf1 to Vf3) that determines the supply amount to the exhaust heat utilization device (4, 5) of warm water flowing through (L2) is provided, and the exhaust heat utilization device (4, 5) A measuring device (temperature sensors St1 to St3) for measuring the temperature of the hot water inlet to the exhaust heat utilization device (4, 5) located in the vicinity of the upstream side of the exhaust heat recovery of the secondary hot water line (L2). Heat exchanger (2) outlet temperature measuring device (temperature sensor St22), waste heat recovery heat exchanger of secondary side hot water line (L2) (2) inlet temperature measuring device (temperature sensor St33), and primary An exhaust heat recovery heat exchanger (2) outlet temperature measuring device (temperature sensor St5) of the side hot water line (L1) and a control device (control unit 8) are provided, and the control device (8) Hot water temperature near the upstream side of the heat utilization equipment (4, 5) Hot water temperature measured at St1 to St3: hot water inlet temperature of exhaust heat utilization device) and exhaust heat recovery heat exchanger (2) outlet temperature of secondary side hot water line (L2) (hot water measured by temperature sensor St22) Temperature: secondary side hot water outlet temperature), exhaust heat recovery heat exchanger (2) inlet temperature of secondary side hot water line (L2) (hot water temperature measured by temperature sensor St33: secondary side hot water inlet temperature), Exhaust heat corresponding to any of the exhaust heat recovery heat exchanger (2) outlet temperature of the primary hot water line (L1) (warm water temperature measured by the temperature sensor St5: primary hot water outlet temperature) The hot water supply amount supplied to the utilization devices (4, 5) is proportionally controlled.

  According to the present invention, the prime mover (1), the exhaust heat recovery heat exchanger (2), and the cooling tower (3) form a circulation channel by the primary side hot water line (L1), and the primary side hot water line (L1) includes a flow path (L13) that bypasses the cooling tower (3), and the exhaust heat recovery heat exchanger (2) and a plurality of exhaust heat utilization devices (4, 5) are connected to the secondary hot water line. (L2) forms a circulation flow path, and the secondary hot water line (L2) includes flow paths (L221, L231) that bypass the plurality of waste heat utilization devices (4, 5), and the secondary side In the cogeneration system in which the bypass flow path (L221, L231) of the hot water line (L2) and the outlet side of the exhaust heat utilization device (4, 5) merge and return to the exhaust heat recovery heat exchanger (2) , Each of the plurality of exhaust heat utilization devices (4, 5) has a secondary hot water line. A hot water supply amount determination device (for example, three-way valves Vf1 to Vf3) that determines the supply amount to the exhaust heat utilization device (4, 5) of warm water flowing through (L2) is provided, and the exhaust heat utilization device (4, 5) A measuring device (temperature sensors St1 to St3) for measuring the temperature of the hot water inlet to the exhaust heat utilization device (4, 5) located in the vicinity of the upstream side of the exhaust heat recovery of the secondary hot water line (L2). Heat exchanger (2) outlet temperature measuring device (temperature sensor St22), waste heat recovery heat exchanger of secondary side hot water line (L2) (2) inlet temperature measuring device (temperature sensor St33), and primary An exhaust heat recovery heat exchanger (2) in the side hot water line (L1) (2) is provided with an inlet temperature measuring device (temperature sensor St4) and a control device (control unit 8). The control device (8) Hot water temperature near the upstream side of the heat utilization equipment (4, 5) Hot water temperature measured at St1 to St3: hot water inlet temperature of exhaust heat utilization device) and exhaust heat recovery heat exchanger (2) outlet temperature of secondary side hot water line (L2) (hot water measured by temperature sensor St22) Temperature: secondary side hot water outlet temperature), exhaust heat recovery heat exchanger (2) inlet temperature of secondary side hot water line (L2) (hot water temperature measured by temperature sensor St33: secondary side hot water inlet temperature), Exhaust heat corresponding to any of the exhaust heat recovery heat exchanger (2) inlet temperature of the primary side hot water line (L1) (warm water temperature measured by the temperature sensor St4: primary side hot water inlet temperature) The hot water supply amount supplied to the utilization devices (4, 5) is proportionally controlled.

In the present invention, when the control device (control unit 8) performs control to increase the valve opening on the side where the secondary hot water is supplied to the exhaust heat utilization device (4, 5) side, the exhaust heat utilization efficiency. When the proportional control is performed from a high exhaust heat utilization device and control is performed to increase the valve opening on the side where the secondary hot water bypasses the exhaust heat utilization device (4, 5), the exhaust having low exhaust heat utilization efficiency is performed. It is preferable that the proportional control is performed from the heat utilization device (FIGS. 15 to 19).
Here, the control device (control unit 8) includes a plurality of waste heat utilization devices (for example, waste heat input type absorption chiller / heaters, water heaters 4 and 5 equipped with heat exchangers, etc.). It is preferable to have an exhaust heat utilization efficiency determining device (81) that determines heat utilization efficiency (FIGS. 15 to 17).
Or the said control apparatus (control unit 8) is the waste heat in each of several waste heat utilization apparatus (For example, the hot water supply type | mold absorption chiller / heater, the hot water heaters 4 and 5 provided with the heat exchanger, etc.). It is preferable to have a storage device (for example, database 9) for storing the utilization efficiency (FIGS. 18 and 19).

  In the present invention, the control device (control unit 8) determines in advance when the supply amount of the hot water flowing through the secondary hot water line (L2) to the exhaust heat utilization equipment (4, 5) is changed. It is preferable that proportional control is performed for each exhaust heat utilization device (4, 5) in accordance with the order in which they are performed (FIG. 20).

  Furthermore, in the present invention, when the control device (control unit 8) performs control to increase the valve opening on the side where the secondary hot water is supplied to the exhaust heat utilization equipment (4, 5) side (the exhaust system). Proportional control is performed from the exhaust heat utilization equipment that has a large effect on the heat generated by the heat utilization equipment 4, 5), and the valve opening on the side where the secondary hot water bypasses the exhaust heat utilization equipment (4, 5) is increased. When performing the control to be performed, it is preferable that the proportional control is performed from the exhaust heat utilization device that is less affected by the generated heat (in the exhaust heat utilization devices 4 and 5) (FIGS. 21 and 22). ).

  In carrying out the present invention, the control device (control unit 8) may be configured as a central processing unit, or a chip embedded in each hot water supply amount determination device (for example, the three-way valves Vf1 to Vf3). A control unit may be used.

  The control method of the cogeneration system according to claim 1 described above is the hot water temperature in the vicinity of the upstream side of the exhaust heat utilization device (4, 5) (the hot water temperature measured by the temperature sensors St1 to St3: the hot water inlet of the exhaust heat utilization device Step (S1) for measuring the temperature) and the hot water temperature in the vicinity of the upstream side of the measured exhaust heat utilization device (4, 5) (hot water temperature measured by the temperature sensors St1 to St3: hot water inlet of the exhaust heat utilization device It is preferable to have a step (S2) of proportionally controlling the amount of hot water supplied to the exhaust heat utilization device (4, 5) corresponding to (temperature) (FIGS. 1 and 2).

  The control method of the cogeneration system according to claim 2 includes a step (S11) of measuring an outlet temperature of the exhaust heat recovery heat exchanger (2) of the secondary side hot water line (L2) and a secondary side hot water line (L2). ) Exhaust heat recovery heat exchanger (2) Hot water supply supplied to the exhaust heat utilization device (4, 5) corresponding to the outlet temperature (warm water temperature measured by the temperature sensor St22: secondary hot water outlet temperature) It is preferable to have a step (S12) of proportionally controlling the amount (FIGS. 3 and 4).

  Alternatively, the control method of the cogeneration system according to claim 3 includes the step (S21) of measuring the exhaust heat recovery heat exchanger (2) inlet temperature of the secondary hot water line (L2) and the secondary hot water line (L2). ) Exhaust heat recovery heat exchanger (2) Hot water supply supplied to the exhaust heat utilization device (4, 5) corresponding to the inlet temperature (warm water temperature measured by the temperature sensor St33: secondary hot water inlet temperature) It is preferable to have a step (S22) of proportionally controlling the amount (FIGS. 5 and 6).

  And the control method of the cogeneration system of Claim 4 measures the process (S31) which measures the exhaust-heat recovery heat exchanger (2) exit temperature of a primary side hot water line (L1), and a primary side hot water line (L1). ) Exhaust heat recovery heat exchanger (2) Hot water supply supplied to the exhaust heat utilization equipment (4, 5) corresponding to the outlet temperature (warm water temperature measured by the temperature sensor St5: primary side hot water outlet temperature) And a step (S32) of proportionally controlling the amount (FIGS. 7 and 8).

  Furthermore, the control method of the cogeneration system according to claim 5 includes a step (S41) of measuring the exhaust heat recovery heat exchanger (2) inlet temperature of the primary side hot water line (L1) and the primary side hot water line (L1). ) Exhaust heat recovery heat exchanger (2) Hot water supply supplied to the exhaust heat utilization equipment (4, 5) corresponding to the inlet temperature (warm water temperature measured by the temperature sensor St4: primary hot water inlet temperature) And a step (S42) of proportionally controlling the amount (FIGS. 9 and 10).

  The control method of the cogeneration system of Claim 6 is measured by the hot water inlet temperature (temperature sensors St1 to St3) to the exhaust heat utilization device (4, 5) in the vicinity of the upstream side of the exhaust heat utilization device (4, 5). Hot water temperature: hot water inlet temperature of exhaust heat utilization equipment) or exhaust heat recovery heat exchanger (2) outlet temperature of secondary side hot water line (L2) (warm water temperature measured by temperature sensor St22: secondary side hot water outlet Temperature), the exhaust heat recovery heat exchanger (2) inlet temperature of the secondary side hot water line (L2) (warm water temperature measured by the temperature sensor St33: secondary side hot water inlet temperature), or the primary side hot water line ( L1) exhaust heat recovery heat exchanger (2) step (S51) of measuring one of the outlet temperatures (hot water temperature measured by temperature sensor St5: primary hot water outlet temperature) and corresponding to the measured temperature Proportional to the amount of hot water supplied to the waste heat utilization equipment Gosuru step (S52), preferably has a capital (11, 12).

  The control method of the cogeneration system of Claim 7 is measured by the hot water inlet temperature (temperature sensor St1-St3) to the waste heat utilization equipment (4, 5) near the upstream side of the waste heat utilization equipment (4, 5). Hot water temperature: hot water inlet temperature of exhaust heat utilization equipment) or exhaust heat recovery heat exchanger (2) outlet temperature of secondary side hot water line (L2) (warm water temperature measured by temperature sensor St22: secondary side hot water outlet Temperature), the exhaust heat recovery heat exchanger (2) inlet temperature of the secondary side hot water line (L2) (warm water temperature measured by the temperature sensor St33: secondary side hot water inlet temperature), or the primary side hot water line ( L1) waste heat recovery heat exchanger (2) step (S61) of measuring one of the inlet temperatures (hot water temperature measured by temperature sensor St4: primary side hot water inlet temperature) and corresponding to the measured temperature Proportional to the amount of hot water supplied to the waste heat utilization equipment Gosuru step (S62), preferably has a capital (13, 14).

In the control method of the cogeneration system according to claim 8, when the control is performed to increase the valve opening on the side where the secondary hot water is supplied to the exhaust heat utilization device (4, 5) side, the exhaust heat utilization efficiency. Control to increase the valve opening on the side (4 or 5) on which the secondary side hot water bypasses the exhaust heat utilization device. When performing, it is preferable to perform proportional control from the exhaust heat utilization equipment (any of 4, 5) with low exhaust heat utilization efficiency (FIGS. 15-19).
Here, if the control device (control unit 8) has a waste heat utilization efficiency determination device (81), a plurality of waste heat utilization devices (for example, a waste heat input type absorption chiller / heater, It is preferable to have the process (S72) which determines the waste-heat utilization efficiency in each of the hot water heaters 4 and 5 provided with the heat exchanger (FIGS. 15-17).
Or if the said control apparatus (control unit 8) has a memory | storage device (for example, database 9) which memorize | stores the waste heat utilization efficiency in each of several waste heat utilization apparatus, the said memory | storage device (9 ) To read the waste heat utilization efficiency of each waste heat utilization device (S93, S95) (FIGS. 18 and 19).

  Further, in the control method of the cogeneration system according to claim 9, a predetermined order is used when the supply amount of the hot water flowing through the secondary hot water line (L2) to the exhaust heat utilization equipment (4, 5) is changed. Accordingly, it is preferable to perform proportional control (S103) for each exhaust heat utilization device (4, 5) (FIG. 20).

  Furthermore, in the control method of the cogeneration system according to claim 10, when control is performed to increase the valve opening on the side where the secondary hot water is supplied to the exhaust heat utilization equipment (4, 5) side (the exhaust heat utilization) Proportional control (S116) is performed from the exhaust heat utilization device (4 or 5), which has a large effect on the generated heat (in the devices 4 and 5), and the secondary hot water is used as the exhaust heat utilization device (4 or 5). When the control is performed to increase the valve opening degree on the bypass side (in any of the exhaust heat utilization devices 4, 5), the exhaust heat utilization device (4, 5 Proportional control (S114) is preferably performed from any one (FIGS. 21 and 22).

  According to the present invention having the above-described configuration, the output of the exhaust heat utilization equipment (4, 5) is stabilized, so that unnecessary equipment, for example, a backup burner of a WAR of an absorption chiller / heater, exhaust heat, etc. Operation of a boiler or the like combined with a water heater using a heat exchanger is suppressed, and auxiliary power can be reduced.

  In addition, since the temperature of the exhaust heat water on the secondary side is stabilized, the exhaust heat temperature on the primary side is also stabilized, the heat radiation from the cooling tower (3) on the primary side is suppressed, and the exhaust heat utilization rate is improved. .

  Further, by using the temperature on the primary side of the exhaust heat recovery heat exchanger (2) for determining the heat radiation to the cooling tower (3) for control, the heat radiation from the cooling tower (3) is surely suppressed. This leads to further improvement of the exhaust heat utilization rate.

  In addition, since exhaust heat can be selectively used from a device with high exhaust heat utilization efficiency, the energy saving performance of the entire system is improved.

  Hereinafter, embodiments of the present invention will be described with reference to FIGS.

First, a first embodiment will be described based on FIG. 1 and FIG.
The first embodiment of FIGS. 1 and 2 is an embodiment in which proportional control is performed instead of the conventional ON-OFF control according to the exhaust heat hot water inlet temperature to the exhaust heat utilization device.

  In FIG. 1, the cogeneration system of the first embodiment includes a prime mover (engine) 1, an exhaust heat recovery heat exchanger 2, a cooling tower 3, and an exhaust heat utilization heat exchanger 41. It has the apparatus 4 and the 2nd waste heat utilization equipment 5 which has the waste heat utilization heat exchanger 51, and the motor | power_engine 1, the waste heat recovery heat exchanger 2, and the cooling tower 3 are the primary side circulation line L1. The exhaust heat recovery heat exchanger 2 and the first exhaust heat utilization device 4 and the second exhaust heat utilization device 5 communicate with each other so as to be circulated by the secondary side circulation line L2. .

The primary side circulation line (engine coolant line) L1 includes a pipe L11 that connects the prime mover 1 and the exhaust heat recovery heat exchanger 2, and a pipe L12 that connects the exhaust heat recovery heat exchanger 2 and the branch point B1. When a pipe L13 to be connected to the branch point B1 to a three-way valve V, a pipe L14 connecting the branch point B1 and a cooling tower 3, a pipe L15 connecting the cooling tower 3 and a three-way valve V, three It is constituted by a pipe L16 which connects the square valve 3 and the prime mover 1.

  The secondary side circulation line (exhaust heat hot water line) L2 includes a pipe L21 connecting the exhaust heat recovery heat exchanger 2 and the first branch point B21, and the first branch point B21 and the first exhaust heat utilization device. A pipe L22 connecting the second branch point B22 on the 4 side, a pipe L221 connecting the second branch point B22 and the three-way valve Vf1 on the first exhaust heat utilization device 4 side, and a second branch point A pipe L222 for connecting B22 and the exhaust heat utilization heat exchanger 41 on the first exhaust heat utilization device 4 side, an exhaust heat utilization heat exchanger 41 on the first exhaust heat utilization device 4 side, and the first exhaust heat. It has a pipe L223 that connects the three-way valve Vf1 on the use device 4 side, and a pipe L224 that connects the three-way valve Vf1 on the first exhaust heat use device 4 side and the first junction G21.

  Further, the secondary circulation line L2 includes a pipe L23 that connects the first branch point B21 and the second branch point B23 on the second exhaust heat utilization device 5 side, a third branch point B23, and a second branch point B23. A pipe L231 connecting the three-way valve Vf2 on the second exhaust heat utilization device 5 side, and a pipe L232 connecting the third branch point B23 and the exhaust heat utilization heat exchanger 51 on the second waste heat utilization device 5 side. A pipe L233 connecting the exhaust heat utilization heat exchanger 51 on the second exhaust heat utilization equipment 5 side and the three-way valve Vf2 on the second exhaust heat utilization equipment 5 side, and the second exhaust heat utilization equipment 5 side The pipe L234 connecting the three-way valve Vf2 and the first junction G21, and the pipe L24 connecting the first junction G21 and the third three-way valve Vf3.

  In addition, the secondary side circulation line L2 includes a pipe L25 connecting the third three-way valve Vf3 and the second junction G22, and the pipe L25 between the third three-way valve Vf3 and the second junction. And a bypass pipe L26 for connecting the second junction G22 and the exhaust heat recovery heat exchanger 2 to the bypass pipe L26.

  Another heat exchanger 6 is interposed in the pipe L25, and is configured to exchange heat with the heat medium circulating in another tertiary heat medium circulation line L3.

  The piping L27 is provided with a circulation pump 7 that pumps exhaust hot water circulating through the secondary circulation line L2.

  That is, the first exhaust heat utilization device 4 and the second exhaust heat utilization device 5 are connected in parallel to the exhaust heat recovery heat exchanger 2 by an exhaust heat hot water line (secondary side: L2). Yes.

  In the primary side circulation line L1, the high-temperature cooling water discharged from the prime mover 1 exchanges heat with the waste heat hot water circulating in the secondary side circulation line L2 in the waste heat recovery heat exchanger 2 (to the waste heat hot water). When the cooled cooling water is sufficiently cooled, it is returned to the prime mover 10 via the pipe L12, the branch point B, the pipe L13, the three-way valve V, and the pipe L16 without passing through the cooling tower 3. .

  On the other hand, when the cooled cooling water is not sufficiently cooled, the cooling water exiting the exhaust heat recovery heat exchanger 2 passes through the cooling tower 3, that is, the pipe L12, the branch point B, the pipe L14, It is returned to the prime mover 1 via the cooling tower 3, the pipe L15, the three-way valve V, and the pipe L16.

  Here, the control of the primary side three-way valve V detects the degree of load on the motor side at that time, the temperature, and the like, and is automatically controlled by a signal from a control means (not shown).

  In the secondary side circulation line L2 (exhaust heat hot water line), the pipes L22 and L23 on the outlet side of the exhaust heat recovery heat exchanger 2 and in the vicinity of the exhaust heat utilization heat exchangers 41 and 51 are provided with temperature sensors St1, St2 is interposed. Further, a temperature sensor St3 is interposed in the return side pipe L24 of the secondary circulation line L2.

  Each of the following embodiments from the first embodiment of the present invention is equipped with a control unit 8 for controlling the flow direction and valve opening of each of the three-way valves Vf1 to Vf3 interposed in the secondary line L2. is doing.

  In the first embodiment, the control unit 8 is connected to the temperature sensors St1, St2, and St3 in the order of signs by the input signal lines Si1, Si2, and Si3, and the control signal line So1, the three-way valves Vf1, Vf2, and Vf3 in the order of signs. They are connected by So2 and So3.

  In the secondary side circulation line L2 (exhaust heat hot water line), the pump 7 is driven, and the exhaust heat hot water heated by the high temperature engine cooling water in the primary circulation line L1 in the exhaust heat recovery heat exchanger 2 is Then, it reaches the branch point B21 via the pipe L21.

The flow on the first exhaust heat utilization device 4 side first flows into the pipe L22 from the first branch point B21. As described above, the temperature sensor St1 is interposed in the pipe L22, and a temperature difference with a tertiary heat medium (not shown) circulating in the exhaust heat utilization heat exchanger 41 is measured, and the control unit 8 is measured. When the temperature of the exhaust heat hot water is higher, the exhaust heat utilization heat exchanger 41 side of the three-way valve Vf1 is opened and the opening degree is set according to the temperature difference, that is, as the temperature difference is larger. Control to increase the opening.
That is, the exhaust heat water that has exited the first branch point B21 passes through the pipe L22, the second branch point B22, the pipe L222, the first exhaust heat utilization heat exchanger 41, the pipe L223, the three-way valve Vf1, and the pipe L224. It reaches to the first confluence G21 via.

  On the other hand, when the temperature of the exhaust heat hot water is lower, the control unit 8 bypasses the exhaust heat utilization heat exchanger 41 so that a reverse flow of heat from the exhaust heat utilization heat exchanger 41 does not occur. That is, the exhaust heat water having exited the first branch point B21 reaches the first junction G21 via the pipe L22, the second branch point B22, the pipe L221, the three-way valve Vf1, and the pipe L224.

The flow on the second exhaust heat utilization device 5 side first flows into the pipe L23 from the first branch point B21. As described above, the temperature sensor St2 is interposed in the pipe L23, and a temperature difference with a tertiary heat medium (not shown) circulating in the exhaust heat utilization heat exchanger 51 is measured, and the control unit 8 is measured. When the temperature of the exhaust heat water is higher, the side of the exhaust heat utilization heat exchanger 51 of the three-way valve Vf2 is opened, and the opening degree is set according to the temperature difference, that is, as the temperature difference is larger. Control to increase the opening.
That is, the exhaust heat water having exited the first branch point B21 passes through the pipe L23, the third branch point B23, the pipe L232, the second exhaust heat utilization heat exchanger 51, the pipe L233, the three-way valve Vf2, and the pipe L234. It reaches to the first confluence G21 via.

  On the other hand, when the temperature of the exhaust heat hot water is lower, the control unit 8 bypasses the exhaust heat utilization heat exchanger 51 so that a reverse flow of heat from the exhaust heat utilization heat exchanger 51 does not occur. That is, the exhaust heat water having exited the first branch point B21 reaches the first junction G21 via the pipe L23, the second branch point B23, the pipe L231, the three-way valve Vf2, and the pipe L234.

Next, the flow of the waste heat hot water from the first junction G21 to the waste heat recovery heat exchanger 2 will be described.
As described above, the temperature sensor St3 is interposed in the pipe L24, and the heat is different from the waste heat hot water discharged from the first waste heat utilization heat exchanger 41 and the second waste heat utilization heat exchanger 51. The control unit 8 measures the temperature difference with another heat medium on the tertiary side circulating in the exchanger 6, and if the temperature of the exhaust heat water is higher, the control unit 8 performs another heat exchange of the three-way valve Vf3. While opening the vessel 6 side, the opening degree is controlled in accordance with the temperature difference, that is, the opening degree is increased as the temperature difference is larger.
In other words, the exhaust heat hot water that has exited the first junction G21 passes through the pipe L24, the three-way valve Vf3, the pipe L25 including another heat exchanger, the second junction G22, and the pipe L27 to recover the exhaust heat. It reaches the exchanger 2.

  On the other hand, when the temperature of the exhaust heat water is lower, the control unit 8 bypasses the heat exchanger 6 so that the reverse flow of heat from another heat exchanger 6 does not occur. Exhaust heat water that has exited the junction G21 reaches the exhaust heat recovery heat exchanger 2 via the pipe L24, the three-way valve Vf3, the pipe (bypass) L26, the second junction G22, and the pipe L27.

With reference to FIG. 2, the control method of 1st Embodiment is demonstrated.
First, the control unit 8 inputs a signal for measuring the hot water temperature of the temperature sensors St1 to St3 (step S1), and corresponding to the measured hot water temperature, the opening pattern and each opening degree of each of the three-way valves Vf1 to Vf3. As described above, when the exhaust heat hot water side is high, proportional control is performed according to the temperature difference. Here, as proportional control, PID or other control (feedback control) may be used, and a map or the like may be used.

  Next, the control unit 8 determines whether or not to continue the control (step S3). If the control is to be terminated (YES in step S3), the control unit 8 is terminated and the control is continued (step S3). NO), returns to step S1, and repeats step S1 and subsequent steps again.

According to the first embodiment described above, the temperature of the exhaust heat hot water measured by the temperature sensor St3 immediately before the heat exchanger 6 is the sensor St1 and the temperature of the exhaust heat utilization device 4, 5 if at least one of them is operating. This is different from the exhaust heat hot water temperature measured at St2. And the backflow of the heat in each waste heat utilization equipment 4 and 5 and the heat exchanger 6 is prevented.
In the illustrated example, the control unit 8 controls the three-way valves Vf1 to Vf3. However, a chip (microcomputer) is embedded in each of the three-way valves Vf1 to Vf3, and the three-way valves Vf1 to Vf3 are independently controlled. Also good.

Next, 2nd Embodiment is described based on FIG.3 and FIG.4.
The second embodiment of FIGS. 3 and 4 is an embodiment in which proportional control is performed according to the exhaust heat hot water outlet temperature on the secondary side L2 of the exhaust heat recovery heat exchanger 2.

  The second embodiment of FIGS. 3 and 4 eliminates all the temperature sensors St1 to St3 from the first embodiment of FIGS. 1 and 2, and instead, is in the immediate vicinity of the outlet of the exhaust heat recovery heat exchanger 2. The difference is that the temperature sensor St22 is interposed in the (piping L21). The temperature sensor St22 is connected to the control unit 8 by an input signal line Si22. Other configurations are the same as those in the first embodiment.

The control of the second embodiment will be described with reference to FIG.
First, the control unit 8 measures the outlet temperature on the secondary side L2 of the exhaust heat recovery heat exchanger 2 by the temperature sensor St (step S11).
In the next step S12, the control unit 8 proportionally controls the opening patterns and the opening degrees of the three-way valves Vf1 to Vf3 in accordance with the hot water temperature measured by the temperature sensor St22.

  Next, the control unit 8 determines whether or not to continue the control (step S13). If the control is to be terminated (YES in step S13), the control unit 8 is terminated as it is, and if the control is to be continued (step S13). NO), returns to step S11, and repeats step S11 and subsequent steps.

3 and 4 described above, the instability of the hot water temperature in the exhaust hot water (secondary hot water) is improved.
As a result of the secondary side hot water being efficiently put into the exhaust heat utilization devices 4 and 5, it is possible to prevent the primary side hot water temperature from suddenly rising during a control transition period or the like, and in the cooling tower 3 on the primary side. Heat dissipation is prevented. In other words, effective use of exhaust heat is guaranteed.

Next, a third embodiment of the present invention will be described based on FIGS.
The third embodiment in FIGS. 5 and 6 is an embodiment in which proportional control is performed according to the exhaust heat hot water inlet temperature on the secondary side L2 of the exhaust heat recovery heat exchanger 2.

  The third embodiment shown in FIGS. 5 and 6 eliminates all the temperature sensors St1 to St3 from the first embodiment shown in FIGS. 1 and 2, and instead, is close to the inlet of the exhaust heat recovery heat exchanger 2. The difference is that the temperature sensor St33 is interposed in the (piping L27). The temperature sensor St33 is connected to the control unit 8 by an input signal line Si33. Other configurations are the same as those in the first embodiment.

The control of the third embodiment will be described with reference to FIG.
First, the control unit 8 measures the inlet temperature on the secondary side L2 of the exhaust heat recovery heat exchanger 2 by the temperature sensor St33 (step S21).
In the next step S22, the control unit 8 proportionally controls the opening patterns and the opening degrees of the three-way valves Vf1 to Vf3 in accordance with the hot water temperature measured by the temperature sensor St33.

  Next, the control unit 8 determines whether or not to continue the control (step S23). If the control is to be terminated (YES in step S23), the control unit 8 is terminated and the control is to be continued (step S23). NO), returns to step S21, and repeats step S21 and subsequent steps again.

  According to the above-described three embodiments of FIGS. 5 and 6, the outlet temperature of each device 4, 5, 6 is not limited, so the amount of exhaust heat input is limited when only one unit is operating. Can be prevented.

Next, a fourth embodiment of the present invention will be described based on FIGS.
7 and 8 is an embodiment in which proportional control is performed according to the exhaust heat hot water outlet temperature on the primary side L1 of the exhaust heat recovery heat exchanger 2.

  The fourth embodiment of FIGS. 7 and 8 eliminates all the temperature sensors St1 to St3, and replaces the primary side of the exhaust heat recovery heat exchanger 2 with respect to the first embodiment of FIGS. The difference is that the temperature sensor St5 is interposed in the immediate vicinity (pipe L12). The temperature sensor St5 is connected to the control unit 8 by an input signal line Si5. Other configurations are the same as those in the first embodiment.

The control of the fourth embodiment will be described with reference to FIG.
First, the control unit 8 measures the outlet temperature on the primary side L1 of the exhaust heat recovery heat exchanger 2 by the temperature sensor St5 (step S31).
In the next step S32, the control unit 8 proportionally controls the opening pattern and each opening degree of the three-way valves Vf1 to Vf3 in accordance with the hot water temperature measured by the temperature sensor St5.

  Next, the control unit 8 determines whether or not to continue the control (step S33). If the control is to be terminated (YES in step S33), the control unit 8 is terminated and the control is to be continued (step S33). NO), returns to step S31, and repeats step S21 and subsequent steps.

In the first to third embodiments (FIGS. 1 to 7), the control is performed based on the secondary hot water temperature. In the above-described fourth embodiment of FIGS. Control based on hot water temperature.
It is the primary side that dissipates heat from the cooling tower 3. Therefore, if the primary side is checked, the exhaust heat may be sufficiently input to the exhaust heat utilization devices 4 and 5 and the heat exchanger 6 when it is necessary to dissipate heat from the radiator tower 3.

  Here, if the three-way valves Vf <b> 1 to Vf <b> 3 are controlled only by the primary-side hot water temperature, there is a risk that the heat flows backward in each exhaust heat utilization device 4, 5, 6. In order to prevent such a situation, when implementing the fourth embodiment of FIGS. 7 and 8, control based on the inlet temperature of the exhaust heat utilization devices 4, 5 and 6 on the secondary side (FIGS. 1 and 2). In combination with the control shown in the first embodiment. (Illustration omitted)

Next, a fifth embodiment of the present invention will be described based on FIG. 9 and FIG.
The fifth embodiment of FIGS. 9 and 10 is an embodiment in which proportional control is performed by the exhaust heat hot water inlet temperature to the primary side of the exhaust heat recovery heat exchanger 2.

  The fifth embodiment of FIGS. 9 and 10 eliminates all the temperature sensors St1 to St3 from the first embodiment of FIGS. 1 and 2 and replaces the primary side of the exhaust heat recovery heat exchanger 2 instead. The difference is that the temperature sensor St4 is interposed in the immediate vicinity (pipe L11). The temperature sensor St4 is connected to the control unit 8 by an input signal line Si4. Other configurations are the same as those in the first embodiment.

The control of the fifth embodiment will be described with reference to FIG.
First, the control unit 8 measures the inlet temperature on the primary side of the exhaust heat recovery heat exchanger 2 by the temperature sensor St4 (step S41).
In the next step S42, the control unit 8 proportionally controls the opening patterns and the opening degrees of the three-way valves Vf1 to Vf3 in accordance with the hot water temperature measured by the temperature sensor St4.

  Next, the control unit 8 determines whether or not to continue the control (step S43). If the control is to be terminated (YES in step S43), the control unit 8 is terminated and the control is continued (step S43). NO), returns to step S41, and repeats step S41 and subsequent steps.

If the three-way valves Vf1 to Vf3 are controlled only by the primary hot water temperature, there is a possibility that the heat flows backward in each of the exhaust heat utilization devices 4, 5, and 6.
In order to prevent such a situation, when the fifth embodiment of FIGS. 9 and 10 is carried out, control based on the inlet temperature of the exhaust heat utilizing devices 4, 5, 6 on the secondary side (FIGS. 1, 2). (Control shown in the first embodiment) is preferably combined (not shown).

Next, based on FIG.11 and FIG.12, 6th Embodiment of this invention is described.
11 and 12 is an embodiment in which the control unit 8 performs proportional control by adding the fourth embodiment to the first to third embodiments described above.

  In FIG. 11, the temperature sensors include temperature sensors St1 to St3, St22, St33, and St5. The temperature sensor St5 is connected to the control unit 8 by an input signal line Si5.

With reference to FIG. 12, the control method of 6th Embodiment is demonstrated.
First, the control unit 8 measures the hot water temperature at each position using the temperature sensors St1 to St3, St22, St33, and St5 (step S51).
In the next step S52, the control unit 8 determines the opening pattern and each opening of the three-way valves Vf1 to Vf3 based on the hot water temperature measured by the temperature sensors St1 to St3, St22, St33 and St5, and proportionally Control (step S52).

  Next, the control unit 8 determines whether or not to continue the control (step S53). If the control is to be terminated (YES in step S53), the control unit 8 is terminated and the control is continued (step S53). NO), returns to step S51, and repeats step S51 and subsequent steps again.

  According to 6th Embodiment mentioned above, there exists an effect equivalent to 1st Embodiment-3rd Embodiment and 4th Embodiment.

Next, a seventh embodiment of the present invention will be described with reference to FIGS.
The seventh embodiment of FIGS. 13 and 14 is an embodiment in which the control unit 8 performs proportional control by adding the fifth embodiment to the first to third embodiments described above.

  In FIG. 13, the temperature sensor includes temperature sensors St1 to St3, St22, St33, and St4.

With reference to FIG. 14, the control method of 7th Embodiment is demonstrated.
First, the control unit 8 measures the hot water temperature at each position by the temperature sensors St1 to St3, St22, St33, and St4 (step S61).
In the next step S62, the control unit 8 determines the opening pattern and the opening degrees of the three-way valves Vf1 to Vf3 based on the hot water temperatures measured by the temperature sensors St1 to St3, St22, St33 and St4, and proportionally Control (step S52).

  Next, the control unit 8 determines whether or not to continue the control (step S63). If the control is to be terminated (YES in step S63), the control unit 8 is terminated and the control is to be continued (step S63). NO), returns to step S61, and repeats step S61 and subsequent steps.

  Although not clearly shown, in the sixth embodiment of FIGS. 11 and 12 and the seventh embodiment of FIGS. 13 and 14, the measurement signals of St1 to St3, St22, St33, St4, and St5 are described. It is also possible to control the valve openings of Vf1 to Vf3 by applying different weights.

Next, based on FIGS. 15-17, 8th Embodiment of this invention is described.
In the eighth embodiment shown in FIGS. 15 to 17, the control unit 8 is combined with any one of the first to seventh embodiments. The control unit 8 bypasses the exhaust heat utilization devices 4 and 5 and the heat exchanger 6. When the flow is changed to the L221, L231, and L26 sides, proportional control is performed in order from the device with the low exhaust heat utilization efficiency. On the other hand, when the flow is changed to the exhaust heat utilization devices 4 and 5 and the heat exchanger 6 side, the proportional control is sequentially performed from the device having the high exhaust heat utilization efficiency.

Here, there are cases where the exhaust heat utilization efficiency (efficiency for converting the input exhaust heat into the required cold temperature and heat) is known in advance or is not known unless it is measured. When it is not known unless it is measured, that is, when the exhaust heat utilization efficiency changes under various conditions, it is necessary to judge each time using a map or the like.
The eighth embodiment of FIGS. 15 to 17 is an embodiment corresponding to such a case.

In FIG. 15, temperature sensors St1 to St3, St22, St33, St4 and St5 are provided as temperature sensors. The control unit 8A is equipped with an exhaust heat utilization efficiency determination device 81. About other than that, it is the same as that of 1st-7th embodiment.
The exhaust heat utilization efficiency is determined by the exhaust heat utilization efficiency determination means 81 provided in the control unit 8A based on calculation or a map according to various parameters of the exhaust heat utilization equipment. Although not clearly shown, parameters necessary for determining the exhaust heat utilization efficiency are measured by a sensor (not shown) and sent to the exhaust heat utilization efficiency determination means.

Next, an example of control according to the eighth embodiment will be described with reference to FIG.
First, parameters necessary for the exhaust heat utilization efficiency are input (step S71), and the exhaust heat utilization efficiency of each exhaust heat utilization device is calculated (step S72). Then, any one of the temperature sensors St1 to St3, St22, St33, St4, and St5 is measured (step S73).

In the next step S74, the control unit 8A determines whether or not to change the opening degree of the three-way valves Vf1 to Vf3. If the opening degree is changed so as to be largely opened to each bypass side, the process proceeds to step S75. If it progresses and the opening degree is changed so as to be largely opened toward the exhaust heat utilization devices 4 and 5 and the heat converter 6, the process proceeds to step S76.
On the other hand, if the opening is not changed (NO in step S74), the process proceeds to step S77.

  In step S75, after proportional control is performed with priority from the exhaust heat utilization device having low exhaust heat utilization efficiency, the process returns to step S71, and step S71 and subsequent steps are repeated again.

  In step S76, after proportional control is performed preferentially from the exhaust heat utilization device having high exhaust heat utilization efficiency, the process returns to step S71, and step S71 and subsequent steps are repeated again.

  In step S78, the control unit 8A determines whether or not to end the control. If the control ends (YES in step S77), the control unit 8A ends as it is and continues the control (NO in step S77). It returns to S71 and repeats after step S71 again.

Next, another example of the control method of the eighth embodiment will be described with reference to FIG.
In FIG. 16, the exhaust heat utilization efficiency is determined regardless of whether or not the opening degrees of Vf1 to Vf3 are changed. On the other hand, in FIG. 17, the exhaust heat utilization efficiency is determined only when the opening degrees of Vf1 to Vf3 are changed.

  First, one of the temperature sensors St1 to St3, St22, St33, St4, and St5 is measured (step S81).

In the next step S82, the control unit 8A determines whether or not to change the opening degree of the three-way valves Vf1 to Vf3. If the opening degree is changed so as to be greatly opened to each bypass side, the process proceeds to step S83. If the opening degree is changed so that the opening degree is greatly opened to the exhaust heat utilization devices 4 and 5 and the heat converter 6 side, the process proceeds to step S86.
On the other hand, if the opening is not changed (NO in step S82), the process proceeds to step S89.

  In step S83, parameters necessary for the exhaust heat utilization efficiency are input, and the exhaust heat utilization efficiency of each exhaust heat utilization device is calculated using a map or the like (step S84). In step S85, proportional control is performed preferentially from the waste heat utilization device having low waste heat utilization efficiency, and then the process returns to step S81, and step S81 and subsequent steps are repeated again.

  In step S86, parameters necessary for the exhaust heat utilization efficiency are input, and the exhaust heat utilization efficiency of each exhaust heat utilization device is calculated using a map or the like (step S87). In step S88, proportional control is performed preferentially from the exhaust heat utilization device having high exhaust heat utilization efficiency, and then the process returns to step S81, and step S81 and subsequent steps are repeated again.

  In step S89, the control unit 8A determines whether or not to end the control. If the control is ended (YES in step S89), the control unit 8A ends the control as it is and continues the control (NO in step S89). It returns to S81 and repeats after step S81 again.

Next, a modification of the eighth embodiment will be described based on FIGS.
The eighth embodiment in FIGS. 15 to 17 is an embodiment in which the exhaust heat utilization efficiency is not known unless it is measured, but in the modification of the eighth embodiment in FIGS. 18 and 19, the exhaust heat utilization efficiency. Is an embodiment in which is known in advance.

  Here, in FIG. 18, the exhaust heat utilization efficiency known in advance is stored in the storage means (database) 9 of the control unit 8. Except for the database 9 being connected to the control unit 8, it is the same as in the first to eighth embodiments.

With reference to FIG. 19, the control method of the modification of 8th Embodiment is demonstrated.
First, one of the temperature sensors St1 to St3, St22, St33, St4, and St5 is measured (step S91).

In the next step S92, the control unit 8 determines whether or not to change the opening degree of the three-way valves Vf1 to Vf3. If the opening degree is changed so as to be greatly opened to each bypass side, the process proceeds to step S93. If it progresses and the opening degree is changed so as to be largely opened toward the exhaust heat utilization devices 4, 5 and the heat converter 6, the process proceeds to step S95.
On the other hand, if the opening is not changed (NO in step S92), the process proceeds to step S97.

  In step S93, the exhaust heat utilization efficiency of each exhaust heat utilization device is read, and after proportional control (step S94) is performed in preference to the exhaust heat utilization device with low exhaust heat utilization efficiency, the process returns to step S91, and again step S91. Repeat thereafter.

  In step S95, the waste heat utilization efficiency of each waste heat utilization device is read and proportional control (step S96) is performed in preference to the waste heat utilization device having a high waste heat utilization efficiency, and then the process returns to step S91 and again step S91. Repeat thereafter.

  In step S97, the control unit 8 determines whether or not to end the control. If the control ends (YES in step S97), the control unit 8 ends the process and continues the control (NO in step S89). It returns to S81 and repeats after step S81 again.

Next, a ninth embodiment will be described based on FIG.
The ninth embodiment of FIG. 20 is an embodiment that performs proportional control in order from the exhaust heat utilization devices 4 and 5 and the heat exchanger 6 specified in advance. The system configuration is the same as the configuration of the modified example of the eighth embodiment (FIG. 18). However, in FIG. 18, which is a block diagram of the eighth embodiment, the storage means 9 of the control unit 8 stores the exhaust heat utilization efficiency (exhaust heat utilization efficiency known in advance) in each exhaust heat utilization device. On the other hand, in the ninth embodiment, the storage unit 9 stores a predetermined “order for performing proportional control (for exhaust heat utilization equipment)”.

  In FIG. 20, first, any one of the temperature sensors St1 to St3, St22, St33, St4, and St5 is measured (step S101).

  In the next step S102, the control unit 8 determines whether or not to change the opening of the three-way valves Vf1 to Vf3, and if so (YES in step S102), according to a predetermined order, After proportionally controlling the amount of exhaust heat flowing into the exhaust heat utilization device (step S103), the process proceeds to step S104. On the other hand, if the opening degree of each of the three-way valves Vf1 to Vf3 is not changed (NO in step S102), the process proceeds to step S104 as it is.

  In step S104, the control unit 8 determines whether or not to end the control, and if it ends (YES in step S104), the control unit 8 ends as it is. On the other hand, if the control is continued (NO in step S104), the process returns to step S101 and repeats step S101 and subsequent steps.

Next, a tenth embodiment will be described based on FIGS. 21 and 22.
The tenth embodiment shown in FIGS. 21 and 22 is configured to reduce the exhaust heat from those having a small influence on the downstream side or the tertiary side of the exhaust heat utilization device (the side using the “desired heat” generated in the exhaust heat utilization device). 1 is an embodiment of a system configured to block (bypass).
That is, in the tenth embodiment, the exhaust heat is input from the one having the great merit on the tertiary side.

  In FIG. 21, the control unit 8B is equipped with a determination device 82 for determining the order of influence on the downstream side of the exhaust heat utilization device. The database 9B stores the order of influence on the downstream side of the exhaust heat utilization device.

Next, a control method according to the tenth embodiment will be described with reference to FIG.
First, any one of the temperature sensors St1 to St3, St22, St33, St4, and St5 is measured (step S111).

In the next step S112, the control unit 8 determines whether or not to change the opening degree of the three-way valves Vf1 to Vf3. If the opening degree is changed so as to be greatly opened to each bypass side, the process proceeds to step S113. If the opening degree is changed so that the opening degree is greatly opened toward the exhaust heat utilization devices 4 and 5 and the heat converter 6, the process proceeds to step S115.
On the other hand, if the opening is not changed (NO in step S112), the process proceeds to step S117.

  In step S113, the order of influence on the downstream side of each exhaust heat utilization device is read, and proportional control (step S114) is performed preferentially from the waste heat utilization device having a small influence on the downstream side, and then the process returns to step S111. Step S111 and subsequent steps are repeated again.

  In step S115, the order of the influence on the downstream side of each exhaust heat utilization device is read, and proportional control (step S116) is performed preferentially from the waste heat utilization device having a large influence on the downstream side, and then the process returns to step S111. Step S111 and subsequent steps are repeated again.

  In step S117, the control unit 8 determines whether or not to end the control. If the control is ended (YES in step S117), the control unit 8 ends as it is and continues the control (NO in step S117). It returns to S111 and repeats after step S111 again.

The illustrated embodiment is merely an example, and is not intended to limit the technical scope of the present invention.
For example, in the embodiment of FIGS. 1 to 14 (first embodiment to seventh embodiment), the central processing using the control unit 8 is performed, but a chip-like control unit is provided for each of the three-way valves Vf1 to Vf3. It is also possible to send the measurement signal of each sensor to the chip-shaped control unit, and determine the valve opening degree on the three-way valves Vf1 to Vf3 exhaust heat utilization equipment side or bypass side by the chip-shaped control unit. .

The block diagram which showed the structure of the cogeneration system of 1st Embodiment of invention. The flowchart which showed the control method of the cogeneration system of 1st Embodiment of this invention. The block diagram which showed the structure of the cogeneration system of 2nd Embodiment. The flowchart which showed the control method of the cogeneration system of 2nd Embodiment. The block diagram which showed the structure of the cogeneration system of 3rd Embodiment. The flowchart which showed the control method of the cogeneration system of 3rd Embodiment. The block diagram which showed the structure of the cogeneration system of 4th Embodiment. The flowchart which showed the control method of the cogeneration system of 4th Embodiment. The block diagram which showed the structure of the cogeneration system of 5th Embodiment. The flowchart which showed the control method of the cogeneration system of 5th Embodiment. The block diagram which showed the structure of the cogeneration system of 6th Embodiment. The flowchart which showed the control method of the cogeneration system of 6th Embodiment. The block diagram which showed the structure of the cogeneration system of 7th Embodiment. The flowchart which showed the control method of the cogeneration system of 7th Embodiment. The block diagram which showed the structure of the cogeneration system of 8th Embodiment. The flowchart which showed the control method of the cogeneration system of 8th Embodiment. The flowchart which showed the other example of the control method of the cogeneration system of 8th Embodiment. The block diagram which showed the structure of the modification of 8th Embodiment of the cogeneration system of this invention. The flowchart which showed the control method of the cogeneration system of the irregular example of 8th Embodiment. The flowchart which showed the other example of the control method of the cogeneration system of 9th Embodiment. The block diagram which showed the structure of the cogeneration system of 10th Embodiment. The flowchart which showed the other example of the control method of the cogeneration system of 10th Embodiment. The block diagram which showed the structure of the cogeneration system in a prior art.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Motor | power_engine 2 ... Waste heat recovery heat exchanger 3 ... Cooling tower 4 ... 1st waste heat utilization apparatus 5 ... 2nd waste heat utilization apparatus 6 ... Heat exchanger 7 ... circulation pump 8 ... control unit 9 ... storage means / database 41 ... first waste heat utilization equipment side waste heat utilization heat exchanger 45 ... second waste heat utilization equipment Side exhaust heat utilization heat exchanger L1... Primary side circulation (warm water) line L2... Secondary side circulation (warm water) lines St1 to St3, St, St22, St33, St4, St5. Vf1 to Vf3 ... Three-way valve

Claims (10)

The prime mover (1), the exhaust heat recovery heat exchanger (2), and the cooling tower (3) form a circulation channel by the primary side hot water line (L1), and the primary side hot water line (L1) A flow path (L13) that bypasses the tower (3) is provided, and the exhaust heat recovery heat exchanger (2) and the plurality of exhaust heat utilization devices (4, 5) are circulated by the secondary hot water line (L2). A path is formed, and the secondary hot water line (L2) includes flow paths (L221, L231) that bypass the plurality of exhaust heat utilization devices (4, 5), and the secondary hot water line (L2) In the cogeneration system in which the bypass passages (L221, L231) and the outlet side of the exhaust heat utilization device (4, 5) join together and return to the exhaust heat recovery heat exchanger (2), the plurality of exhaust heats Each of the used devices (4, 5) flows through the secondary hot water line (L2). There are provided hot water supply amount determining devices (Vf1 to Vf3) for determining the supply amount of the hot water to the plurality of exhaust heat utilization devices (4, 5), and the vicinity of the upstream side of the exhaust heat utilization devices (4, 5). Are provided with measuring devices (St1 to St3) for measuring the temperature of the hot water inlet to the plurality of waste heat utilization devices (4, 5), and upstream of the plurality of waste heat utilization devices (4, 5). A control device (8) configured to proportionally control the amount of hot water supplied to the plurality of exhaust heat utilization devices (4, 5) corresponding to the temperature of hot water near the side is provided. Cogeneration system. The prime mover (1), the exhaust heat recovery heat exchanger (2), and the cooling tower (3) form a circulation channel by the primary side hot water line (L1), and the primary side hot water line (L1) A flow path (L13) that bypasses the tower (3) is provided, and the exhaust heat recovery heat exchanger (2) and the plurality of exhaust heat utilization devices (4, 5) are circulated by the secondary hot water line (L2). A path is formed, and the secondary hot water line (L2) includes flow paths (L221, L231) that bypass the plurality of exhaust heat utilization devices (4, 5), and the secondary hot water line (L2) In the cogeneration system in which the bypass passages (L221, L231) and the outlet side of the exhaust heat utilization device (4, 5) join together and return to the exhaust heat recovery heat exchanger (2), the plurality of exhaust heats Each of the used devices (4, 5) flows through the secondary hot water line (L2). Hot water supply amount determination devices (Vf1 to Vf3) for determining the supply amount to the hot water waste heat utilization equipment (4, 5) are provided, and the exhaust heat recovery heat exchanger ( 2) An outlet temperature measuring device (St22) is provided, and a waste heat recovery heat exchanger (2) of the secondary hot water line (L2) (2) waste heat utilization device (4, 5) corresponding to the outlet temperature Has a control device (8) configured to proportionally control the amount of hot water supplied to the. The prime mover (1), the exhaust heat recovery heat exchanger (2), and the cooling tower (3) form a circulation channel by the primary side hot water line (L1), and the primary side hot water line (L1) A flow path (L13) that bypasses the tower (3) is provided, and the exhaust heat recovery heat exchanger (2) and the plurality of exhaust heat utilization devices (4, 5) are circulated by the secondary hot water line (L2). A path is formed, and the secondary hot water line (L2) includes flow paths (L221, L231) that bypass the plurality of exhaust heat utilization devices (4, 5), and the secondary hot water line (L2) In the cogeneration system in which the bypass passages (L221, L231) and the outlet side of the exhaust heat utilization device (4, 5) join together and return to the exhaust heat recovery heat exchanger (2), the plurality of exhaust heats Each of the used devices (4, 5) flows through the secondary hot water line (L2). Hot water supply amount determination devices (Vf1 to Vf3) for determining the supply amount to the hot water waste heat utilization equipment (4, 5) are provided, and the exhaust heat recovery heat exchanger ( 2) An inlet temperature measuring device (St33) is provided, and an exhaust heat utilization device (4, 5) corresponding to the exhaust heat recovery heat exchanger (2) inlet temperature of the secondary hot water line (L2) A cogeneration system comprising a control device (8) configured to proportionally control the amount of hot water supplied to the water. The prime mover (1), the exhaust heat recovery heat exchanger (2), and the cooling tower (3) form a circulation channel by the primary side hot water line (L1), and the primary side hot water line (L1) A flow path (L13) that bypasses the tower (3) is provided, and the exhaust heat recovery heat exchanger (2) and the plurality of exhaust heat utilization devices (4, 5) are circulated by the secondary hot water line (L2). A path is formed, and the secondary hot water line (L2) includes flow paths (L221, L231) that bypass the plurality of exhaust heat utilization devices (4, 5), and the secondary hot water line (L2) In the cogeneration system in which the bypass passages (L221, L231) and the outlet side of the exhaust heat utilization device (4, 5) join together and return to the exhaust heat recovery heat exchanger (2), the plurality of exhaust heats Each of the used devices (4, 5) flows through the secondary hot water line (L2). Hot water supply amount determination devices (Vf1 to Vf3) for determining the supply amount to the hot water exhaust heat utilization equipment (4, 5) are provided, and the exhaust heat recovery heat exchanger (V1) on the primary side hot water line (L1) ( 2) An outlet temperature measuring device (St5) is provided and supplied to the exhaust heat utilization equipment (4, 5) corresponding to the exhaust heat recovery heat exchanger outlet temperature of the primary hot water line (L1). A cogeneration system comprising a control device (8) configured to proportionally control the amount of hot water supplied. The prime mover (1), the exhaust heat recovery heat exchanger (2), and the cooling tower (3) form a circulation channel by the primary side hot water line (L1), and the primary side hot water line (L1) A flow path (L13) that bypasses the tower (3) is provided, and the exhaust heat recovery heat exchanger (2) and the plurality of exhaust heat utilization devices (4, 5) are circulated by the secondary hot water line (L2). A path is formed, and the secondary hot water line (L2) includes flow paths (L221, L231) that bypass the plurality of exhaust heat utilization devices (4, 5), and the secondary hot water line (L2) In the cogeneration system in which the bypass passages (L221, L231) and the outlet side of the exhaust heat utilization device (4, 5) join together and return to the exhaust heat recovery heat exchanger (2), the plurality of exhaust heats Each of the used devices (4, 5) flows through the secondary hot water line (L2). Hot water supply amount determination devices (Vf1 to Vf3) for determining the supply amount to the hot water exhaust heat utilization equipment (4, 5) are provided, and the exhaust heat recovery heat exchanger (V1) on the primary side hot water line (L1) ( 2) An inlet temperature measuring device (St4) is provided and the exhaust heat recovery heat exchanger (2) of the primary hot water line (L1) (2) waste heat utilization equipment (4, 5) corresponding to the inlet temperature A cogeneration system comprising a control device (8) configured to proportionally control the amount of hot water supplied to the water. The prime mover (1), the exhaust heat recovery heat exchanger (2), and the cooling tower (3) form a circulation channel by the primary side hot water line (L1), and the primary side hot water line (L1) A flow path (L13) that bypasses the tower (3) is provided, and the exhaust heat recovery heat exchanger (2) and the plurality of exhaust heat utilization devices (4, 5) are circulated by the secondary hot water line (L2). A path is formed, and the secondary hot water line (L2) includes flow paths (L221, L231) that bypass the plurality of exhaust heat utilization devices (4, 5), and the secondary hot water line (L2) In the cogeneration system in which the bypass passages (L221, L231) and the outlet side of the exhaust heat utilization device (4, 5) join together and return to the exhaust heat recovery heat exchanger (2), the plurality of exhaust heats Each of the used devices (4, 5) flows through the secondary hot water line (L2). Hot water supply amount determination devices (Vf1 to Vf3) for determining the supply amount to the hot water waste heat utilization equipment (4, 5) are provided and are located in the vicinity of the upstream side of the waste heat utilization equipment (4, 5). Measuring device (St1 to St3) for measuring the hot water inlet temperature to the exhaust heat utilization equipment (4, 5), and the exhaust heat recovery heat exchanger (2) outlet temperature measuring device for the secondary hot water line (L2) (St22), exhaust heat recovery heat exchanger of the secondary side hot water line (L2) (2) inlet temperature measuring device (St33), and exhaust heat recovery heat exchanger of the primary side hot water line (L1) (2 ) An outlet temperature measuring device (St5) and a control device (8) are provided, and the control device (8) includes a hot water temperature in the vicinity of the upstream side of the exhaust heat utilization device (4, 5), a secondary Waste heat recovery heat exchanger (2) outlet temperature of the side hot water line (L2) and waste heat recovery heat of the secondary side hot water line (L2) Corresponding to either the inlet temperature of the exchanger (2) and the outlet heat recovery heat exchanger (2) outlet temperature of the primary side hot water line (L1), it is supplied to the exhaust heat utilization equipment (4, 5). A cogeneration system that is configured to proportionally control the amount of hot water supplied. The prime mover (1), the exhaust heat recovery heat exchanger (2), and the cooling tower (3) form a circulation channel by the primary side hot water line (L1), and the primary side hot water line (L1) A flow path (L13) that bypasses the tower (3) is provided, and the exhaust heat recovery heat exchanger (2) and the plurality of exhaust heat utilization devices (4, 5) are circulated by the secondary hot water line (L2). A path is formed, and the secondary hot water line (L2) includes flow paths (L221, L231) that bypass the plurality of exhaust heat utilization devices (4, 5), and the secondary hot water line (L2) In the cogeneration system in which the bypass passages (L221, L231) and the outlet side of the exhaust heat utilization device (4, 5) join together and return to the exhaust heat recovery heat exchanger (2), the plurality of exhaust heats Each of the used devices (4, 5) flows through the secondary hot water line (L2). Hot water supply amount determination devices (Vf1 to Vf3) for determining the supply amount to the hot water waste heat utilization equipment (4, 5) are provided and are located in the vicinity of the upstream side of the waste heat utilization equipment (4, 5). Measuring device (St1 to St3) for measuring the hot water inlet temperature to the exhaust heat utilization equipment (4, 5), and the exhaust heat recovery heat exchanger (2) outlet temperature measuring device for the secondary hot water line (L2) (St22), exhaust heat recovery heat exchanger of the secondary side hot water line (L2) (2) inlet temperature measuring device (St33), and exhaust heat recovery heat exchanger of the primary side hot water line (L1) (2 ) An inlet temperature measuring device (St4) and a control device (8) are provided. The control device (8) is connected to the hot water temperature in the vicinity of the upstream side of the exhaust heat utilization device (4, 5) and the secondary temperature. Waste heat recovery heat exchanger (2) outlet temperature of the side hot water line (L2) and waste heat recovery heat of the secondary side hot water line (L2) In response to any of the heat exchanger (2) inlet temperature of the exhaust heat recovery heat exchanger (2) at the inlet temperature, the hot water supply amount supplied to the exhaust heat utilization equipment (4, 5) is proportionally controlled. A cogeneration system characterized by being configured. When the control device (8) performs control to increase the valve opening on the side where the secondary hot water is supplied to the exhaust heat utilization device (4, 5) side, the exhaust heat utilization device having high exhaust heat utilization efficiency. Proportional control is performed, and proportional control is performed from the waste heat utilization device with low waste heat utilization efficiency when performing control to increase the valve opening on the side where the secondary hot water bypasses the waste heat utilization device (4, 5). The cogeneration system according to any one of claims 1 to 7, wherein the cogeneration system is configured to perform the following. When the supply amount of the hot water flowing through the secondary hot water line (L2) to the exhaust heat utilization device (4, 5) is changed, the control device (8) uses the exhaust heat according to a predetermined order. The cogeneration system according to any one of claims 1 to 7, wherein the cogeneration system is configured to perform proportional control for each device (4, 5). When the control device (8) performs control to increase the valve opening degree on the side where the secondary hot water is supplied to the exhaust heat utilization device (4, 5) side, the exhaust heat that has a great influence on the generated heat is exerted. When proportional control is performed from the equipment used and control is performed to increase the valve opening on the side where the secondary hot water bypasses the waste heat utilization equipment (4, 5), the use of waste heat is less affected by the generated heat. The cogeneration system according to any one of claims 1 to 7, wherein the cogeneration system is configured to perform proportional control from a device.

Images