WO2021053965A1 - 熱回収装置 - Google Patents

熱回収装置 Download PDF

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Publication number
WO2021053965A1
WO2021053965A1 PCT/JP2020/028173 JP2020028173W WO2021053965A1 WO 2021053965 A1 WO2021053965 A1 WO 2021053965A1 JP 2020028173 W JP2020028173 W JP 2020028173W WO 2021053965 A1 WO2021053965 A1 WO 2021053965A1
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WO
WIPO (PCT)
Prior art keywords
heat recovery
preheating
heat exchanger
water
supply water
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2020/028173
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English (en)
French (fr)
Japanese (ja)
Inventor
岳廣 松坂
真克 岡谷
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Industrial Equipment Systems Co Ltd
Original Assignee
Hitachi Industrial Equipment Systems Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hitachi Industrial Equipment Systems Co Ltd filed Critical Hitachi Industrial Equipment Systems Co Ltd
Priority to CN202080063441.XA priority Critical patent/CN114375382B/zh
Priority to JP2021546531A priority patent/JP7367040B2/ja
Priority to US17/639,005 priority patent/US12092113B2/en
Priority to EP20865648.8A priority patent/EP4033098B1/en
Publication of WO2021053965A1 publication Critical patent/WO2021053965A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/123—Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/08—Cooling; Heating; Preventing freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D17/00—Domestic hot-water supply systems
    • F24D17/0005—Domestic hot-water supply systems using recuperation of waste heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • F25B31/008—Cooling of compressor or motor by injecting a liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/004—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/80—Diagnostics
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D2200/00—Heat sources or energy sources
    • F24D2200/16—Waste heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D2200/00—Heat sources or energy sources
    • F24D2200/16—Waste heat
    • F24D2200/30—Friction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D2220/00—Components of central heating installations excluding heat sources
    • F24D2220/02—Fluid distribution means
    • F24D2220/0271—Valves

Definitions

  • the present invention relates to a heat recovery device.
  • the heat recovery heat exchanger is provided in the air passage from the compressor to the air cooler, and heat exchange between the compressed air and water to produce hot water.
  • the air passage from the compressor to the heat recovery heat exchanger and the air passage from the heat recovery heat exchanger to the air cooler are connected by a bypass path.
  • the compressed air passes through the air passage, the compressed air passes through the heat recovery heat exchanger, and during that time, the water introduced from the water supply passage is heated by the heat of the compressed air to produce hot water.
  • Patent Document 1 the cooling water channel and the water supply channel are separated, and heat exchange between these water channels is not intended.
  • the temperature of the cooling water after passing through the air cooler rises, but it is only stated that it is cooled by the cooling tower, passes through the cooling water channel again, and is passed to the air cooler, and heat is transferred from the hot water after passing through the air cooler. No attempt has been made to recover it.
  • the water from the water supply source passes through the heat recovery heat exchanger through the water supply channel and becomes hot water in the meantime, but the water temperature before passing through the heat recovery heat exchanger is the cooling water after passing through the air cooler. It is also assumed that the temperature is lower than that.
  • Patent Document 1 does not make such a reference.
  • Patent Document 1 does not consider that a liquid such as water can be preheated and then heated again by a heat recovery heat exchanger to supply a higher temperature liquid.
  • An object of the present invention is to preheat the supply water and then heat it again with a heat recovery heat exchanger to supply a higher temperature supply water.
  • the heat recovery device of one aspect of the present invention is a heat recovery device connected to at least one compressor, and includes an auxiliary cooling heat exchanger that performs auxiliary cooling and a heat recovery exchanger that heats supply water.
  • a preheating heat exchanger that preheats the supply water and supplies it to the heat recovery exchanger, a supply water path that supplies the supply water to the heat recovery exchanger, and a branch from the supply water path.
  • the preheating heat exchanger has a preheating bypass path for supplying the supply water to the preheating heat exchanger and returning the supply water preheated by the preheating heat exchanger to the supply water path. It is characterized in that the cooling water on the outlet side of the auxiliary cooling heat exchanger and the supply water passing through the preheating bypass path exchange heat with each other.
  • the heat recovery device of one aspect of the present invention is a heat recovery device connected to at least one compressor, and includes an auxiliary cooling heat exchanger that performs auxiliary cooling and a heat recovery exchanger that heats supply water.
  • a preheating heat exchanger that preheats the supply water and supplies it to the heat recovery exchanger, a supply water path that supplies the supply water to the heat recovery exchanger, and a branch from the supply water path.
  • the preheating heat exchanger has a preheating bypass path for supplying the supply water to the preheating heat exchanger and returning the supply water preheated by the preheating heat exchanger to the supply water path. It is characterized in that the cooling water supplied from the outside through the cooling water path and the supplied water passing through the preheating bypass path exchange heat with each other.
  • the supply water can be preheated and then heated again by the heat recovery heat exchanger to supply a higher temperature supply water.
  • FIG. It is a system diagram which shows the heat recovery system of Example 1.
  • FIG. It is a graph which shows the effect obtained by a heat recovery system.
  • FIG. 1 shows a system diagram of a heat recovery system. Moreover, the effect obtained by Example 1 will be described with reference to FIG. Further, Example 1 shows an example in which the present invention is applied to a water-cooled oil-free screw compressor as a compressor unit.
  • the oil-free screw compressor shown in FIG. 1 is configured to suck in gas (air in this embodiment), compress it, and discharge it.
  • the compressor unit 001 is a single-stage compressor 100 that sucks air through an air path 401, compresses it to a predetermined pressure, and discharges it, and a water-cooled type that cools the discharged high-temperature compressed air.
  • the aftercooler 202 is provided.
  • a discharge air temperature sensor 501 for measuring the temperature of the discharged high-temperature compressed air is installed on the air path 401 downstream of the compressor 100.
  • the compressor 100 and a water-cooled oil cooler 203 for cooling the lubricating oil for lubricating the drive mechanism are provided, and the lubricating oil is supplied to each part through the lubricating oil path 203 as needed inside the compressor unit 001. Is circulated.
  • the compressor 100 and the oil cooler 203 are usually cooled by cooling water passing through the oil cooler cooling path 404 branching from the first cooling water path 402 and the first cooling water path 402, and the cooling in the first cooling water path 402 is performed. Water is circulated by a separately installed pump (not shown), and heat is discharged to the outside by a cooling tower (not shown).
  • the pump and the cooling tower are jointly used with the existing equipment other than the compressor unit 001 and the heat recovery unit 002 described later, and unless the user requires the required specifications, the compressor unit 001 or the compressor unit 001 or The heat recovery unit 002 does not directly control the operation of the pump or the cooling tower.
  • the heat recovery unit 002 constitutes a heat recovery device.
  • the heat recovery unit 002 is attached to the compressor unit 001.
  • the heat recovery unit 002 includes a heat recovery heat exchanger 205, an auxiliary cooling heat exchanger 206, a preheating heat exchanger 207, a circulation pump 103, a temperature control valve 302, a control valve 303, and heat recovery. It includes a cooling water temperature sensor 504 for recovering heat of cooling water, a cooling water outlet temperature sensor 505, and a supply water temperature sensor 506.
  • the suction side of the circulation pump 103 is connected to the high temperature fluid side outlet side of the heat recovery heat exchanger 205. Further, the discharge side of the circulation pump 103 and the cooling water inlet side of the aftercooler 202 in the compressor unit 001 are connected, and the cooling water outlet side of the aftercooler 202 and the high temperature side fluid inlet of the heat recovery heat exchanger 205 are connected.
  • the second cooling water path 403 is formed by being connected to the side.
  • a water supply valve 306 is arranged on the discharge side of the circulation pump 103 of the second cooling water path 403. The water supply valve 306 operates in conjunction with the start of operation of the compressor unit 001, and is always open during the operation of the compressor unit 001.
  • the supply water path 407 is a path for supplying a liquid such as relatively low temperature water from the outside, and heat recovery on the second cooling water path 403 where the temperature has risen after cooling the high temperature compressed air with the aftercooler 202. This is a route that exchanges heat with high-temperature cooling water that passes through the high-temperature fluid side of the heat exchanger 205, is heated, and returns to an external hot water demand destination.
  • the liquid circulating in the supply water path 407 is not particularly limited in its use, and examples thereof include preheating of boiler water supply, hot water heating, and water that can be widely used such as a shower.
  • a temperature control valve 302 is provided at the high temperature fluid side outlet of the heat recovery heat exchanger 205.
  • a cooling water temperature sensor 504 for heat recovery is provided on the downstream side of the temperature control valve 302, and the opening of the valve becomes smaller as the temperature measured by the cooling water temperature sensor 504 for heat recovery increases, and a predetermined heat recovery occurs.
  • THC cooling water control temperature
  • the auxiliary cooling bypass path 406 branches from between the heat recovery heat exchanger 205 outlet and the temperature control valve 302 on the second cooling water path 403, and passes through the high temperature fluid side path of the auxiliary cooling heat exchanger 206. It joins between the downstream side of the temperature control valve 302 on the second cooling water path 403 and the cooling water temperature sensor 504 for heat recovery.
  • the temperature control valve 302 automatically adjusts the opening degree according to the heat recovery cooling water temperature TH2 measured by the heat recovery cooling water temperature sensor 504, and the cooling water in the second cooling water path 403 (heat recovery cooling). Part or all of the water) flows through the auxiliary cooling bypass path 406.
  • the low-temperature cooling water cooled by the cooling tower is supplied to the low-temperature fluid side path of the auxiliary cooling heat exchanger 206 through the third cooling water path 405, and the high temperature has passed through the auxiliary cooling bypass path 406. Heat exchange is performed between the cooling water of the above and the low-temperature cooling water that has passed through the third cooling water path 405.
  • the temperature regulating valve 302 is fully closed, the second After passing through the heat recovery heat exchanger 205, the entire amount of the cooling water on the cooling water path 403 is additionally cooled by the auxiliary cooling heat exchanger 206, and returns to the second cooling water path 403.
  • sufficiently cooled cooling water is supplied to the aftercooler 202, and the purpose is to keep the compressed air temperature at the outlet of the aftercooler 202 below a certain temperature at all times.
  • the high temperature fluid side path inlet of the preheating heat exchanger 207 is connected downstream from the low temperature fluid side path outlet of the auxiliary cooling heat exchanger 206 on the third cooling water path 405, and the auxiliary cooling heat exchanger 206 and A cooling water outlet temperature sensor 505 is installed between the preheating heat exchangers 207.
  • the preheating bypass path 409 branches off from the low temperature fluid side inlet of the heat recovery heat exchanger 205, and again via the low temperature fluid side path of the preheating heat exchanger 207. , It merges downstream from the branch point and upstream from the low temperature fluid side inlet of the heat recovery heat exchanger 205. Further, a control valve 303 is provided on the outlet side of the preheating heat exchanger 207 on the preheating bypass path 407. A supply water temperature sensor 506 is provided on the upstream side of the branch point at which the preheating bypass path 409 branches from the supply water path 407.
  • the direction in which the high-temperature fluid and the low-temperature fluid flow is a countercurrent type that can increase the amount of heat exchanged.
  • a certain supply water flows from the B end to the A end of the heat recovery heat exchanger 205.
  • the temperature at the end of the heat recovery heat exchanger 205A of the high temperature fluid was fixed under the conditions of the prior art and the first embodiment, and the low temperature fluid (supply water) in the first embodiment was fixed.
  • the temperature at the end of the heat exchanger 205B for heat recovery was given by adding the temperature of the preheated portion of the supply water to the temperature of the prior art.
  • the temperature difference between the high temperature fluid and the low temperature fluid on the A end side and the B end side is set to be the same.
  • the equipment at the hot water demand destination that uses the supplied water can use the hot water at a higher temperature than the case where the preheating is not performed, and it is expected that the applications in which the hot water can be used will be expanded. ..
  • the first cooling water system 402 and the third cooling water system 405 do not necessarily have to form independent circuits.
  • a cooling tower (not shown) for cooling the cooling water is shared with each other, and the first cooling water system 402 and the third cooling water system are branched from a common path from the outlet of the cooling tower to the heat recovery system of the present invention. It has no effect on the functionality of Example 1.
  • the heat exchanger method is not limited to a specific method, but with respect to the preheating heat exchanger 207, the temperature difference between the cooling water which is a high temperature fluid and the supply water which is a low temperature fluid is not so large, so that the amount of heat exchanged is increased. It is more preferable to use a plate heat exchanger in which the external dimensions of the heat exchanger are relatively small and the heat transfer area can be increased so that the number of heat exchangers can be increased.
  • the heat recovery system of the first embodiment includes a compressor 100 that compresses the sucked gas and discharges the compressed gas, an aftercooler 202 that cools the compressed gas, and an oil cooler 203 that cools the lubricating oil.
  • the first cooling water path 402 that supplies cooling water to the compressor 100 and the oil cooler 203, and the second cooling water that circulates the cooling water between the aftercooler 202 and the heat recovery heat exchanger 205 by the circulation pump 103.
  • a supply water path 407 that exchanges heat with the high-temperature cooling water in the second cooling water path 406 via the path 403 and the heat recovery heat exchanger 205, and a heat recovery heat exchange on the second cooling water path 406.
  • An auxiliary cooling heat exchanger 206 for cooling the temperature downstream from the outlet of the vessel 205 with the cooling water of the third cooling water path 405 to a temperature that does not interfere with the operation of the compressor 100 is provided, and the auxiliary cooling heat is provided. It is a heat recovery system provided with an auxiliary cooling bypass path 406 that bypasses the cooling water to the exchanger 206.
  • the supply water that has passed through 409 exchanges heat with each other via the preheating heat exchanger 207.
  • the measured value T C2 of the temperature sensor 505 provided in the auxiliary cooling heat exchanger 206 exit on the third cooling water passage 405, a temperature sensor 506 provided upstream from the branching point of the preheating bypass path 409
  • the control valve 303 provided on the preheating bypass path 409 on the outlet side of the preheating heat exchanger 207 is opened.
  • the heat recovery system in the heat recovery system for recovering the heat of the compressed gas from the water-cooled gas compressor, the heat recovery system is supplied to be used as hot water with the cooling water whose temperature has risen after cooling. It is possible to supply higher temperature supply water by exchanging heat with each other via a heat exchanger and preheating the supply water and then heating it again with the heat recovery heat exchanger of the heat recovery system. To do. As a result, the heat recovery rate of the heat recovery system can be improved by recovering heat from a low-temperature heat source that normally only exhausts heat.
  • FIG. 3 is a system diagram of the heat recovery system.
  • the portions having the same reference numerals as those in FIG. 1 indicate the same or corresponding portions, and the description of the same portions as in the first embodiment will be omitted.
  • the compressor unit 001 is provided with a low-pressure stage compressor 101, a high-pressure stage compressor 102, and an intercooler 201 for cooling the compressed air discharged from the low-pressure stage compressor 101.
  • a two-stage oil-free air compressor is used is shown. This configuration is suitable for a relatively large compressor unit that discharges a larger volume of compressed air than the single-stage compressor unit described in the first and second embodiments.
  • the first cooling water system 402 branches to the oil cooler system 404 on the way, and the cooling water is passed through the compressor 101 and the compressor 102.
  • the cooling water discharged from the circulation pump 103 is passed through the intercooler 201 first, and then through the aftercooler 202.
  • the intercooler 201 and the aftercooler 202 receive heat from the compressed air in two stages and send it to the heat recovery heat exchanger 205.
  • the hot water temperature that can be taken out is higher than that of the water passing method shown in Example 1. It can be done, and the amount of heat recovered increases. At this time, the amount of heat entering the high temperature fluid side of the auxiliary cooling heat exchanger 206 via the auxiliary cooling bypass system 406 also increases, and as a result, the amount of heat received by the cooling water on the third cooling water path 405 also increases. Therefore, as compared with the case of the first embodiment, the cooling water of the supply water path 407 having a larger flow rate can be preheated via the preheating heat exchanger 207.
  • the cooling water of the second cooling water path 403 it is desirable that the cooling water is passed through the intercooler 201 before the aftercooler 202.
  • the higher the cooling capacity of the intercooler 201 the more the compressed air is cooled and the smaller the volume. Therefore, the pressure loss that occurs before flowing into the high-pressure compressor 102 can be suppressed to a small value, and the power consumption of the high-pressure compressor 102 can be reduced.
  • the compressed air in the low-pressure stage passing through the intercooler 201 is cooled with low-temperature cooling water as compared with the case where water is passed through the aftercooler 202 first. Can be done. Therefore, it is possible to prevent the cooling performance of the intercooler 201 from deteriorating and to minimize the influence on the performance of the compressor unit 001 as a whole.
  • FIG. 4 is a system diagram of the heat recovery system.
  • the parts having the same reference numerals as those in FIGS. 1 and 3 indicate the same or corresponding parts, and the same parts as those in the first and second embodiments will be omitted.
  • Example 3 has a configuration in which the third cooling water path 405 branches from the first cooling water path 402 in the upstream portion of the heat recovery unit 002. That is, the first cooling water path 402 and the third cooling water path 405 are supplied with low-temperature cooling water from a common cooling tower outside.
  • the third cooling water path 405 joins the equipment inside the compressor unit 001 with the first cooling water path 402 after cooling, downstream of the auxiliary cooling heat exchanger 206. From the same confluence, the bypass path 410 branches and joins the first cooling water path downstream from the high temperature fluid side outlet of the preheating heat exchanger 207.
  • a control valve 304 is installed on the bypass path 410. Further, a check valve 305 is provided at the outlet of the auxiliary cooling heat exchanger 206 on the third cooling water path 405, and the cooling water of the first cooling water path 402 that has become hot is moved to the third cooling water path 405 side. Prevent backflow.
  • the cooling water outlet temperature sensor 505 is installed from the position described in Examples 1 and 2 between the confluence of the first cooling water path and the third cooling water path and the inlet of the preheating heat exchanger 207.
  • the control valve 303 When the cooling water outlet temperature T C2 is higher than the feed water supply temperature T U1, the control valve 303 is opened, the control valve 304 is closed, perform the preheating of the supply water.
  • the control valve 304 When the cooling water outlet temperature T C2 is lower than the feed water supply temperature T U1 is the control valve 303 is closed, the control valve 304 is opened, it does not perform the preheating of the supply water.
  • the control valve 303 is closed, the control valve 304 opens Therefore, it is controlled so that the supply water is not preheated.
  • the cooling water in the first cooling water path cools the oil cooler 203, the low-pressure stage compressor 101, and the high-pressure stage compressor 102. Therefore, in the case of the single-stage compressor unit 001 shown in the first embodiment. A larger amount of heat can be recovered, and the temperature rise due to preheating can be further increased in combination with the amount of heat received from the auxiliary cooling heat exchanger 206 by the cooling water in the third cooling water path, or a larger flow rate of supply water can be obtained. Can be preheated.
  • the supply water can be preheated only while the temperature control valve 302 bypasses the heat recovery cooling water to the auxiliary cooling heat exchanger 206.
  • the high-temperature cooling water of the first cooling water circuit 402 can be passed through the preheating heat exchanger 207 even while the temperature control valve 302 is not bypassed. Preheating becomes possible more effectively.
  • the cooling water temperature of the first cooling water path 402 after cooling the compressor unit 001 becomes abnormally high for some reason, the preheating of the supply water becomes excessive, and as a result, the heat exchanger 205 for heat recovery And the cooling water for the heat recovery water in the auxiliary cooling heat exchanger 206 is insufficiently cooled.
  • the temperature of the heat recovery for cooling water supplied to the compressor unit 001 is higher than the cooling water upper producing temperature T H2, for heat recovery, cooling performance is lowered in intercooler 201, generates a defect in the compressor unit 001 there is a possibility.
  • the control valve 303 is closed, the control valve 304 is opened, and the preheating of the supply water is performed. It is controlled not to be performed.
  • Heat recovery coolant upper limit temperature T HL to prevent hunting of the valve or the like, the temperature temperature regulating valve in consideration slightly higher than the thermal recovery cooling water control temperature T HC of temperature at which the fully closed tolerance Set.
  • the control valve 303 can switch between water flow and water stoppage between one common direction and the remaining two directions among the three-way fluid paths. It is a three-way valve and is installed at the confluence of the supply water path 407 and the preheating bypass path 409 on the outlet side of the preheating heat exchanger 207.
  • the control valve 303 is controlled to control the supply water.
  • the entire amount of the supply water flowing through the path 407 may be passed through the preheating heat exchanger 207, preheated, and reheated by the heat recovery heat exchanger 205.
  • the control valve 303 is similarly controlled, the preheating heat exchanger 207 side is stopped, and the entire amount of supplied water is passed through the heat recovery heat exchanger 205. ..
  • the present invention is not limited to the above-described embodiment, and includes various modifications.
  • an example in which the present invention is applied to an oil-free screw compressor has been described, but the present invention is not limited to this, and the same applies to an oil-cooled screw compressor or a water-injection screw compressor.
  • any fluid machine such as a scroll compressor, a roots blower, or a supercharger can be similarly applied.
  • the intercooler 201 and the aftercooler 202 are connected in series on the second cooling water path 403, but these may be connected in parallel.
  • the order of passing the cooling water on the first cooling water path 402 is typical and is not necessarily limited to this order.
  • the high-pressure stage compressor 102 is first passed through and then the low-pressure stage compressor is compressed.
  • the order of passing water to the machine 101 may be used.
  • the preheating heat exchanger 207 is configured to be built in the heat recovery unit 002, but the function is not affected even if it is separately placed outside the heat recovery unit 002.
  • the first cooling water path and the third cooling water path are described as independent for convenience, but as in the third embodiment, the external cooling tower is shared to recover the heat. Even if the third cooling water path branches off from the first cooling water path outside the system and joins each other again, the function of the present invention is not affected.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compressor (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Fluid Mechanics (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
PCT/JP2020/028173 2019-09-18 2020-07-20 熱回収装置 Ceased WO2021053965A1 (ja)

Priority Applications (4)

Application Number Priority Date Filing Date Title
CN202080063441.XA CN114375382B (zh) 2019-09-18 2020-07-20 热回收装置
JP2021546531A JP7367040B2 (ja) 2019-09-18 2020-07-20 熱回収装置
US17/639,005 US12092113B2 (en) 2019-09-18 2020-07-20 Heat recovery device
EP20865648.8A EP4033098B1 (en) 2019-09-18 2020-07-20 Heat recovery device

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2019169215 2019-09-18
JP2019-169215 2019-09-18

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WO2021053965A1 true WO2021053965A1 (ja) 2021-03-25

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EP (1) EP4033098B1 (https=)
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WO (1) WO2021053965A1 (https=)

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EP4033098A1 (en) 2022-07-27
JPWO2021053965A1 (https=) 2021-03-25
US12092113B2 (en) 2024-09-17
CN114375382B (zh) 2023-10-24
US20220341426A1 (en) 2022-10-27
CN114375382A (zh) 2022-04-19
EP4033098A4 (en) 2024-02-21
EP4033098B1 (en) 2025-04-09
JP7367040B2 (ja) 2023-10-23

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