JP4557793B2 - Waste heat power generator - Google Patents

Description

  The present invention relates to an exhaust heat power generation apparatus that generates power using a relatively low temperature exhaust heat as a heat source and collects electric power, and particularly relates to easy and effective control of the circulation amount of a working medium. The present invention relates to an exhaust heat power generation apparatus capable of improving performance and particularly reducing the size of a steam generator.

  There exists a thing of the structure shown in FIG. 1 as a waste heat power generator. As shown in the figure, the exhaust heat power generation layer includes a steam generator 101, a turbine 102, a condenser 103, a buffer tank 104, and a working medium circulation pump 105, and these devices are connected by a pipe 106. A gas-liquid separator 107 is disposed between the steam generator 101 and the turbine. In addition, 108 is a three-way valve and 109 is a check valve.

  The exhaust heat medium (for example, hot water) 201 is recovered from the exhaust heat source by the steam generator 101 to generate a high-pressure working medium vapor 203 as a working medium. The high-pressure working medium steam 203 is supplied to the turbine 102 to drive the turbine 102, and the turbine 102 drives a generator (not shown). The low-pressure working medium vapor 204 that has become low pressure by driving the turbine 102 is cooled by the external cooling medium (for example, cooling water) 202 in the condenser 103 and becomes a condensate of the working medium. The condensate is stored in the buffer tank 104 and sent to the steam generator 101 by the working medium circulation pump 105.

  In the exhaust heat power generation apparatus having the above configuration, the heat exchanger is required to be downsized from the viewpoint of installation space and cost. However, when the heat exchanger, in particular, the steam generator 101 (or boiler) is downsized, the flow rate of the medium in the steam generator 101 increases, and the pressure loss of the medium circulating in the steam generator 101 increases. It becomes difficult to circulate by circulation. That is, in the exhaust heat power generation apparatus having the gas-liquid separator 107, the liquid column height necessary for returning (recirculating) the separated separated liquid (working medium liquid) 206 to the steam generator 101 is increased. This cannot be ensured.

  When the liquid column height necessary for returning the separation liquid 206 separated by the gas-liquid separator 107 as described above into the steam generator 101 cannot be secured, as shown in FIG. It is common to use a medium recirculation pump 120 that forcibly returns the working medium liquid to the steam generator 101. In general, the medium recirculation pump 120 pumps the separated liquid (working medium liquid) 206 separated by the gas-liquid separator 107 into the steam generator 101 (lower part). However, since the medium recirculation pump 120 needs to suck in and circulate the working medium liquid at a high temperature and close to the saturation pressure, it needs heat resistance and low NPSH (actual suction head) characteristics. Even if it is expensive and provided, problems such as cavitation during operation may occur. 2, the same reference numerals as those in FIG. 1 denote the same or corresponding parts, and the same applies to other drawings.

  In order to deal with the above problem, an exhaust heat power generation apparatus having the configuration shown in FIG. 3 has been proposed by the inventors of the present patent application. As shown in FIG. 3, this exhaust power generation apparatus guides the working medium liquid separated in the gas-liquid separator 107 to the condenser 103 via the pipe 106, and the heat recovery device 111 is connected to the working medium return pipe 110. The condensate (working medium liquid) 205 sent to the steam generator 101 by the working medium circulation pump 105 is sent to the heat recovery unit 111, and the heat of the separation liquid (working medium liquid) 206 from the gas-liquid separator 107 is provided. The working medium liquid sent to the steam generator 101 is heated and heat is recovered. Thus, by recovering the heat of the working medium liquid from the gas-liquid separator 107 by the heat recovery unit 111, the working medium recirculation pump or the like is not provided, and the apparatus is miniaturized without significantly reducing the efficiency. That is, by providing the heat recovery device 111, downsizing is achieved while suppressing a decrease in efficiency. In FIG. 3, 112 is an orifice, and 113 is a preheater.

  However, even in the exhaust heat power generation apparatus having the configuration shown in FIG. 3, the liquid level in the gas-liquid separator 107 disappears (the separated liquid 206 disappears), and the working medium vapor generated in the steam generator 101 is converted into the heat recovery device 111 or When so-called blow-through occurs in the condenser 103, the output of the exhaust heat power generation device is greatly reduced. Therefore, the liquid level of the separated liquid 206 in the gas-liquid separator 107 is controlled within a certain range to prevent blow-through. Must. This is the same even when the separated liquid in the gas-liquid separator 107 is sent to the condenser 103 without providing the heat recovery device 111.

  More specifically, when the liquid level in the gas-liquid separator 107 is lost and the working medium vapor enters the heat recovery unit 111, the working medium vapor is condensed in the heat recovery unit 111. This heat heats the working medium liquid sent to the steam generator 101 and recovers the heat. Therefore, although the heat loss is small, the amount of steam introduced into the turbine 102 decreases by the amount of steam blown through. That is, the temperature of the working medium introduced into the steam generator 101 rises, the heat transfer temperature difference of the steam generator 101 decreases, and the output decreases. Needless to say, when the heat recovery device 111 is not provided or when the steam escapes to the condenser 103, the efficiency decreases.

  In general, the heat transfer efficiency of the steam generator 101 increases as the flow rate of the working medium increases. However, if the working medium amount is too large, the working medium that does not vaporize increases, and the steam generation amount decreases or the working medium is circulated. Auxiliary machinery power increases to make it. That is, the circulating amount of the working medium in the steam generator 101 has an optimum value, but generally it is appropriate to circulate by about 10 to 20% more than the generated steam amount. However, it is not easy to control the circulating amount of the working medium to an optimum value. This is because the amount of steam generated varies depending on the temperature and pressure conditions at that time, and the amount of steam generated is difficult to measure. The same can be said for the case where the amount of generated steam is replaced by the amount of recovered heat, although it is somewhat easier.

  The present invention has been made in view of the above points, and prevents the working medium vapor from being blown from the gas-liquid separator to the heat recovery unit or the condenser with simple control, and the working medium in the steam generator 101. An object of the present invention is to provide an exhaust heat power generation apparatus capable of controlling the amount of circulation roughly appropriately.

  In order to solve the above-described problem, an invention described in claim 1 is directed to a steam generator that recovers exhaust heat to generate high-pressure working medium steam of a working medium, a turbine that expands the high-pressure working medium steam, A condenser for condensing the low-pressure steam and a working medium circulation pump for circulating the working medium, these devices are connected by a working medium circulation path, and a gas-liquid separator is disposed between the steam generator and the turbine. In the exhaust heat power generator configured to drive a generator with the turbine, a circulation amount control means for controlling a circulation amount for circulating a working medium from the condenser to the steam generator is provided, and the gas-liquid separation is performed. The liquid level detection means for detecting the separation liquid level in the vessel is provided, the separated liquid separated by the gas-liquid separator is guided to the condenser via the flow rate control means, and the gas-liquid detected by the liquid level detection means Minute in separator Liquid level and controlling the circulation amount of the working medium by the circulation quantity control means to be a predetermined level.

  According to a second aspect of the present invention, in the exhaust heat power generator according to the first aspect, the steam is generated from the separated liquid and the condenser in a path for guiding the separated liquid from the gas-liquid separator to the condenser. The heat recovery device is provided as a heat exchanger for exchanging heat with the working medium sent to the vessel.

  According to the first aspect of the present invention, the separation liquid in the gas-liquid separator detected by the liquid level detection means is guided to a predetermined level while the separation liquid in the gas-liquid separator is guided to the condenser via the flow rate control means. Since the circulation amount of the working medium is controlled by the circulation amount control means so as to reach a level, the liquid level in the gas-liquid separator is always at a predetermined level, so that the working medium vapor cannot be blown, and the working medium vapor is wasted. Therefore, the circulating amount of the working medium can be maintained at an appropriate amount.

  According to the second aspect of the present invention, heat is exchanged between the separated liquid and the working medium sent from the condenser to the steam generator in a path for guiding the separated liquid from the gas-liquid separator to the condenser. Since the heat recovery unit, which is an exchanger, is provided, it is possible to reduce the size of the apparatus without using an expensive recirculation pump that returns the working medium separation liquid of the gas-liquid separator to the steam generator. No trouble occurs. In addition, since the working medium liquid entering the steam generator is preheated by the heat recovery device, the amount of sensible heat with low heat transfer performance is reduced, and the steam generator can be downsized.

  Embodiments of the present invention will be described below with reference to the drawings. FIG. 4 is a diagram showing a schematic system configuration of the exhaust heat power generator according to the present invention. This exhaust heat power generation device is a power generation device of a closed system, and is a power generation device using a so-called Rankine cycle. The power generation apparatus recovers exhaust heat of an exhaust heat medium (for example, exhaust gas at about 200 ° C. to 400 ° C. or exhaust hot water at 60 ° C. to 100 ° C.) 201 from an external exhaust heat source to generate a high pressure working medium vapor as a working medium A steam generator 11 that generates 203, a turbine (expander) 13 that is driven by expanding the high-pressure working medium steam 203, and a turbine generator 14 that includes a generator 12 that is driven by the turbine 13, The condenser 15 that cools the low-pressure working medium vapor 204 after driving the turbine 13 with an external cooling medium (for example, cooling water or outside air) 202 to form a condensate 205, and the condensate condensed in the condenser 15 A working medium circulation pump 16 that pressurizes and feeds 205 to the steam generator 11 is provided, and these are connected to the steam generator 11, the turbine 13, the condenser 15, and the working medium circulation pump 16. It is connected by the circulation path 17.

Here, HFC123 or trifluoroethanol (CF ₃ CH ₂ OH), which is a low boiling point medium, is used as the working medium. Accordingly, a relatively low-temperature heat source such as exhaust gas having a relatively low temperature (about 200 ° C. to 400 ° C.) or exhaust water having a relatively low temperature (60 ° C. to 100 ° C.) is used. The high-pressure working medium vapor 203 is converted, whereby the turbine 13 directly connected to the generator 12 of the turbine generator 14 can be rotationally driven to generate electric power. Here, the working medium is a low boiling point medium, but may be a high boiling point medium.

  In the exhaust heat power generator, the working medium circulation pump 16 feeds the condensate 205 of the working medium of the condenser 15 to the steam generator 11. The condensate 205 receives the heat energy of the exhaust heat medium 201 by the steam generator 11 and evaporates to a high pressure working medium vapor 203. The high-pressure working medium steam 203 is sent to the turbine 13 directly connected to the generator 12 of the turbine generator 14 where the turbine 13 is driven by the expansion of the high-pressure working medium steam to drive (rotate) the generator 12 to generate power. To do. The low-pressure working medium vapor 204 discharged from the turbine 13 is cooled in the condenser 15 by an external cooling medium 202 such as cooling water, condensed, and cooled by a subcooler (not shown) as necessary. The liquid 205 is sucked into the working medium circulation pump 16 and goes through the closing and system.

  A gas-liquid separator 18 is provided in the working medium circulation path 17 that connects the steam generator 11 and the turbine 13 of the turbine generator 14, and the working liquid separated liquid 206 separated by the gas-liquid separator 18 is operated. It is led to the heating side (recovered side) of the heat recovery unit 20 via the medium return pipe 19 and further led to the condenser 15 via the orifice 21 and the control valve 22. Condensate (working medium liquid) 205 from the condenser 15 sent to the steam generator 11 by the working medium circulation pump 16 flows on the heated side (recovery side) of the heat recovery unit 20. Heated (heat recovered) with the separated liquid 206 from the liquid separator 18, and sent to the steam generator 11. Orifice 21 can be substituted by a pressure loss of a narrow tube or heat recovery unit 20. Further, the heat recovery unit 20 may be omitted. 45 is a pressure gauge for detecting the pressure of the high-pressure working medium steam 203 at the outlet of the steam generator 11, 46 is a thermometer for detecting the temperature of the high-pressure working medium steam 203, 47 is a bypass valve, and 48 is a shut-off valve. .

  When the heat recovery unit 20 is used, it is preferable that the orifice 21 be closer to the condenser 15 of the heat recovery unit 20 because the working medium (liquid) flowing through the orifice 21 does not vaporize (flush). Here, if the separated liquid 206 from the gas-liquid separator 18 is sufficiently cooled by the heat recovery unit 20, instead of returning to the condenser 15, returning to the suction port of the working medium circulation pump 16, Heat loss can be reduced. Instead of the condenser 15, it may be returned anywhere as long as it is a low pressure part of the working medium circulation system including the working medium circulation path 17.

  The gas-liquid separator 18 is provided with a liquid level detector 23 so that the rise and fall of the liquid level of the separation liquid 206 in the gas-liquid separator 18 can be detected. The working medium circulation pump 16 for supplying the working medium (liquid) to the steam generator 11 can arbitrarily control the rotation speed by an inverter. Thereby, the feed amount of the working medium to the steam generator 11 can be freely controlled. As means for freely controlling the feed amount of the working medium, a variable speed pump may be used instead of the combination of the inverter and the pump, or a control valve or the like may be provided at the discharge port of the pump.

  Here, the supply amount of the working medium from the condenser 15 to the steam generator 11 is controlled by the measurement result of the liquid level of the liquid level detector 23 provided in the gas-liquid separator 18. That is, when an increase in the liquid level of the separation liquid 206 in the gas-liquid separator 18 is detected, the rotational speed of the working medium circulation pump 16 is decreased to reduce the feed amount. When a decrease is detected, the working medium circulation pump Control is performed to increase the feed amount by increasing the rotational speed of 16. Thereby, first, the liquid level of the separation liquid 206 in the gas-liquid separator 18 is maintained at a predetermined level, and the steam generated in the steam generator 11 does not blow through the condenser 15 and the like. In this way, the relationship between the amount of steam generated and the amount of condensate 205 supplied to the steam generator 11 under the condition that the liquid level of the separation liquid 206 in the gas-liquid separator 18 is kept constant. Is considered.

  A part of the condensate (working medium liquid) 205 supplied to the steam generator 11 is vaporized to become working medium vapor (high pressure working medium vapor 203), and the working medium vaporized by the gas-liquid separator 18 is the working medium vapor. The working medium liquid (separated liquid 206) is separated, the working medium vapor is sent to the turbine 13 of the turbine generator 14, and the working medium liquid passes through the heat recovery unit 20, the orifice 21 and the control valve 22 from the working medium return pipe. And returned to the condenser 15. Here, the turbine 13 is driven by the steam pressure difference at the inlet / outlet, but naturally, the steam flow rate increases if the pressure difference is large, and decreases if the pressure difference is small. Strictly speaking, there is a relationship such as the rotational speed and torque of the generator 12, but it can be considered that the flow rate of the working medium vapor passing through the turbine 13 is proportional to the pressure difference. Therefore, the steam generation amount of the steam generator 11 may be proportional to the pressure difference at the inlet and outlet of the turbine 13.

  Further, the flow rate of the working medium liquid (separated liquid 206) that passes through the heat recovery device 20 and the orifice 21 and is returned to the condenser 15 is proportional to the square root of the pressure difference before and after the orifice 21, but the pressure before and after the orifice 21. In practice, the difference may be considered the same as the pressure difference at the inlet / outlet of the turbine 13. Therefore, if the pressure difference (turbine inlet / outlet pressure difference) between the outlet of the steam generator 11 and the condenser 15 is taken on the horizontal axis, the working medium steam flow rate, the separated liquid flow rate (mass flow rate), and the sum thereof are shown in FIG. As shown.

  As described above, if the liquid level of the separation liquid 206 in the gas-liquid separator 18 is maintained at a predetermined level, the flow rate of the working medium sent to the steam generator 11 is as shown in FIG. It is equal to the total flow rate C of the flow rate A and the working medium vapor flow rate B. Therefore, if the diameter of the orifice 21 is designed so that the total flow rate C is always 10 to 20% larger than the generated steam amount, the steam generator 11 always has 10 to 20% larger than the generated steam amount. The working medium is supplied, and the supply amount of the working medium is always maintained appropriately.

  When the supply amount of the working medium is controlled by the liquid level of the separation liquid 206 of the gas-liquid separator 18, if the liquid level can be detected by an analog value by the liquid level detector 23, the operation is performed by so-called PID control or the like. The rotational speed of the medium circulation pump 16 may be controlled. However, if the lowering and raising of the liquid level are detected by a general level switch or the like, the fluctuation of the liquid level is suppressed by controlling as follows. be able to.

  (1) While the rise in the liquid level of the separation liquid 206 is detected, the rotational speed of the working medium circulation pump 16 is reduced by a certain amount. While the lowering is detected, the rotational speed of the working medium circulation pump 16 is increased by a certain amount.

  (2) When an increase in the liquid level of the separation liquid 206 is detected, the rotation speed of the working medium circulation pump 16 is temporarily reduced by a certain amount every certain time while the separation liquid 206 is detected. When the lowering is detected, the rotational speed of the working medium circulation pump 16 is increased by a certain amount every certain time while it is detected.

(3) When the liquid level of the separation liquid 206 returns to the appropriate range, half of the correction amount added in (2) above is returned. That is, when the rotational speed is increased in (2), half of the increased amount is reduced. When the rotational speed is decreased, half of the decreased amount is increased.

  By controlling as described above, it is possible to maintain a stable liquid level to some extent without using an expensive analog type liquid level detector for the liquid level detector 23. In (3) above, whether it is reduced or increased, it is not a half amount, but may be a value roughly proportional to the correction amount added in (2) above. Different proportional constants may be used. Moreover, it is good also as a fixed value irrespective of the increased / decreased quantity.

  In this embodiment, since the lubricating oil may accumulate near the liquid level of the separation liquid 206 of the gas-liquid separator 18, the lubricating oil is collected and returned to the lubricating oil system as will be described in detail later. A return pipe 44 is provided. In the case of the present exhaust heat power generation device, when lubricating oil is mixed into the working medium system including the working medium circulation path 17, the lubricating oil remains without being vaporized even when heated in the steam generator 11. It tends to accumulate near the liquid level of the vessel 18. Therefore, in the present exhaust heat power generator operating to keep the liquid level in the gas-liquid separator 18 constant, the control valve 49 starts from the vicinity of the liquid level of the separation liquid 206 of the gas-liquid separator 18 as will be described in detail later. By periodically collecting the lubricating oil, the lubricating oil mixed in the working medium system can be easily collected. In this case, in order to prevent the accumulated lubricating oil from returning to the condenser while the power generation device is stopped, the control valve 22 is an automatic valve, and the gas-liquid separator 18 is used while the device is stopped or for some reason. When the liquid level inside falls, it is good to close.

  In the present embodiment, the liquid level detector 24 is also provided at the outlet of the condenser 15. This is to prevent the working medium in the condenser 15 from being lost and cavitation from occurring in the working circulation pump. Specifically, when the working medium in the condenser 15 runs out, the rotational speed of the working medium circulation pump 16 is reduced or stopped, and the process waits for the liquid level in the condenser 15 to recover.

  In the exhaust heat power generator having the configuration shown in FIG. 4, the main shaft of the turbine generator 14 is supported by bearings 25 and 26. The bearings 25 and 26 are pressurized with the lubricating oil 207 stored in the lubricating oil tank 28 by the lubricating oil supply pump 27 and supplied to the bearings 25 and 26 through the lubricating oil circulation path 34 and the control valve 50. The The lubricating oil that has lubricated and cooled the bearings 25 and 26 is heated, heated, stored in the lubricating oil receptacles 29 and 30, and returned to the lubricating oil tank 28 through the lubricating oil circulation path 34. Note that a dust removing lubricating oil filter 32 and a flow meter 33 are provided on the lubricating oil circulation path 34 on the outlet side of the lubricating oil supply pump 27. Further, the inside of the lubricating oil tank 28 and the inside of the condenser 15 are communicated with each other via a control valve 38 by a working medium vapor return pipe 37. Further, the inside of the lubricating oil tank 28 and the inside of the turbine generator 14 communicate with each other via a pressure equalizing pipe 51 and a control valve 52.

  A temperature regulator (apparatus) 31 is disposed in a pipe (lubricant oil circulation path 34) on the discharge port side of the lubricant supply pump 27, and the condenser 15 is supplied to the temperature regulator 31 by a working medium circulation pump 16 as a cooling medium. Temperature of the lubricating oil supplied to the bearings 25 and 26 by supplying the condensate 205 from the cooling medium pipe 35 and supplying the high-pressure working medium steam 203 from the steam generator 11 as the heating medium through the heating medium pipe 39. Is maintained in a desirable range. A device (such as a thermometer) for measuring the temperature of the lubricating oil 207 is provided between the temperature regulator 31 and the bearings 25 and 26. When the temperature of the lubricating oil 207 rises above a certain value, it is provided in the heating medium pipe 39. The control valve 40 is adjusted in the closing direction, and when the temperature of the lubricating oil 207 falls below a certain value, the control valve 41 of the cooling medium pipe 35 is adjusted in the closing direction. The temperature can be adjusted by.

  Here, the position where the device (thermometer or the like) for measuring the temperature of the lubricating oil 207 is preferably located between the temperature regulator 31 and the bearings 25 and 26, but between the bearings 25 and 26 and the lubricating oil tank 28. There may be. The condensate 205 from the condenser 15 supplied to the temperature controller 31 is returned to the condenser 15 through the working medium return pipe 36. The working medium return pipe 36 is provided with an orifice 53 for controlling the flow rate.

  Further, in the present exhaust heat power generator, a lubricating oil tank 28 is provided in a lubricating oil circulation path 34 for supplying lubricating oil to the bearings 25 and 26 of the turbine generator 14 and is integrally formed in the lubricating oil tank 28. An oil regenerator 42 is provided, and an oil droplet separator 43 formed integrally with the top is provided. The lubricating oil 207 that has been heated by cooling and lubricating the bearings 25 and 26 of the turbine generator 14 is guided to the oil regenerator 42 and is contained in the lubricating oil 207 by coming into contact with the gas phase in the lubricating oil tank 28. The working medium is vaporized and separated. In order to vaporize the working medium in the lubricating oil 207, it is desirable that the temperature of the lubricating oil 207 is high, and it is desirable that the pressure in the oil regenerator 42 is low.

  In the lubricating oil circulation system, the temperature of the lubricating oil 207 is highest immediately after the bearings 25 and 26 are cooled, so that the oil regenerator 42 returns to the portion where the lubricating oil 207 from the bearings 25 and 26 returns. The oil regenerator 42 preferably communicates with the condenser 15, and the working medium vapor return pipe 37 communicates the inside of the condenser 15 and the lubricating oil tank 28. The temperature controller 31 keeps the temperature of the lubricating oil 207 within a desired range. The vaporized working medium is removed by the oil drop separator 43 and returned to the condenser 15 through the working medium vapor return pipe 37 and the control valve 38.

  The separated liquid 206 separated by the gas-liquid separator 18 is sent to the condenser 15 through the working medium return pipe 19, and the lubricating oil mixed in the separated liquid 206 is heated by the steam generator 11. Therefore, it is separated from the working medium vapor by the gas-liquid separator 18 and returned to the inlet of the steam generator 11 through the working medium return pipe 19 and the condenser 15. Therefore, during normal operation, the lubricating oil mixed in the working medium is collected in the steam generator 11, and the concentration of the lubricating oil is highest separated from the high-pressure working medium vapor 203 by the gas-liquid separator 18. The working medium liquid (separation liquid 206) is obtained. Therefore, in the present exhaust heat power generator, the lubricating oil collected around the liquid level of the separated liquid 206 of the gas-liquid separator 18 is periodically passed through the lubricating oil return pipe 44 by the opening / closing layer of the control valve 49, and the oil regenerator of the lubricating oil tank 28. By returning to 42, the lubricating oil 207 is recovered.

  Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various modifications can be made within the scope of the technical idea described in the claims and the specification and drawings. Is possible.

It is a figure which shows the structural example of the conventional waste heat power generator. It is a figure which shows the structural example of the conventional waste heat power generator. It is a figure which shows the structural example of the conventional waste heat power generator. It is a figure which shows the structural example of the waste heat power generator which concerns on this invention. It is a figure which shows the relationship between the turbine inlet / outlet pressure difference and working-medium flow volume of the exhaust heat power generator which concerns on this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 11 Steam generator 12 Generator 13 Turbine 14 Turbine generator 15 Condenser 16 Working medium circulation pump 17 Working medium circulation path 18 Gas-liquid separator 19 Working medium return piping 20 Heat recovery device 21 Orifice 22 Control valve 23 Liquid level detector 24 Liquid level detector 25 Bearing 26 Bearing 27 Lubricating oil supply pump 28 Lubricating oil tank 29 Lubricating oil receiving tray 30 Lubricating oil receiving tray 31 Temperature controller 32 Lubricating oil filter 33 Flowmeter 34 Lubricating oil circulation path 35 Cooling medium piping 36 Working medium return Piping 37 Working medium vapor return pipe 38 Control valve 39 Heating medium piping 40 Control valve 41 Control valve 42 Oil regenerator 43 Oil drop separator 44 Lubricating oil return pipe 45 Pressure gauge 46 Thermometer 47 Bypass valve 48 Shut-off valve 49 Control valve 50 Control valve 51 Pressure equalizing piping 52 Control valve 53 Orifice

Claims (2)

A steam generator that recovers exhaust heat to generate a high-pressure working medium vapor of the working medium, a turbine that expands the high-pressure working medium steam, a condenser that condenses the low-pressure steam from the turbine, and a working medium that circulates Exhaust heat comprising a working medium circulation pump, connecting these devices through a working medium circulation path, arranging a gas-liquid separator between the steam generator and the turbine, and driving a generator by the turbine In the power generator,
A circulation amount control means for controlling a circulation amount for circulating the working medium from the condenser to the steam generator, and a liquid level detection means for detecting a separation liquid level in the gas-liquid separator;
The separation liquid separated by the gas-liquid separator is guided to the condenser through the flow rate control means, and the separation liquid level in the gas-liquid separator detected by the liquid level detection means is set to a predetermined level. An exhaust heat power generator characterized in that the circulation amount of the working medium is controlled by a circulation amount control means. The exhaust heat power generator according to claim 1,
A heat recovery unit that is a heat exchanger for exchanging heat between the separation liquid and a working medium sent from the condenser to the steam generator is provided in a path for guiding the separation liquid from the gas-liquid separator to the condenser. An exhaust heat power generator characterized by that.

Images