WO2018198459A1 - Système de compresseur - Google Patents

Système de compresseur Download PDF

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Publication number
WO2018198459A1
WO2018198459A1 PCT/JP2018/002843 JP2018002843W WO2018198459A1 WO 2018198459 A1 WO2018198459 A1 WO 2018198459A1 JP 2018002843 W JP2018002843 W JP 2018002843W WO 2018198459 A1 WO2018198459 A1 WO 2018198459A1
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WO
WIPO (PCT)
Prior art keywords
compressor
exhaust
control device
compressor system
exhaust air
Prior art date
Application number
PCT/JP2018/002843
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English (en)
Japanese (ja)
Inventor
正彦 高野
善平 竹内
Original Assignee
株式会社日立産機システム
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 株式会社日立産機システム filed Critical 株式会社日立産機システム
Priority to JP2019515097A priority Critical patent/JP6808823B2/ja
Publication of WO2018198459A1 publication Critical patent/WO2018198459A1/fr

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Classifications

    • 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
    • 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
    • F04B39/08—Actuation of distribution members
    • 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
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • F25B27/02—Machines, plants or systems, using particular sources of energy using waste heat, e.g. from internal-combustion engines
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A30/00—Adapting or protecting infrastructure or their operation
    • Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
    • Y02A30/274—Relating to heating, ventilation or air conditioning [HVAC] technologies using waste energy, e.g. from internal combustion engine

Definitions

  • the present invention relates to a compressor system, and relates to a compressor system that uses exhaust heat from a fluid machine that compresses gas.
  • a compressor that compresses gas and discharges compressed gas
  • an expander that expands compressed gas to generate rotational power, and the like are known.
  • a gas compressor includes a compressor body that compresses a gas such as air, a cooling system that absorbs heat generated by compression, a motor that is a driving force source of the compressor, and the like.
  • a gas compressor if the motor input power is 100%, the amount of heat absorbed in the cooling system is equivalent to 90% or more of that, and usually the amount of heat is released to the outside air, and a great deal of energy is consumed. It is discharged to the outside of the compressor body and gas compressor. In order to increase energy efficiency, higher efficiency of the compressor body and the motor is being promoted, but the ratio of the released heat energy is still large, and effective use of exhaust heat is desired.
  • Patent Document 1 uses a steam to drive a compressor and uses heat generated by the compressor to preheat water (feed water) supplied to the boiler to reduce energy consumption in the boiler. Is disclosed.
  • Patent Document 2 discloses that in an air compressor in which a main body case, a compressor main body, a cooler, and a cooler fan are accommodated, air that is blown through the cooler and passes through the air is heated in the main body case.
  • a configuration is disclosed that includes an exhaust duct that leads upward, and includes a door that covers the opening of the side wall of the exhaust duct so as to be freely opened and closed.
  • the technique of utilizing an air compressor as a heating apparatus by opening a door at the time of cold is disclosed.
  • the heat of the warm air discharged from the compressor to the outside generally reaches a high temperature of, for example, 60 ° C. or more.
  • the thing of patent document 2 utilizes a compressor exhaust heat as a warm air, but the exhaust heat which generate
  • the structure is opened to the outside of the body case. Therefore, the temperature of the hot air discharged from the opening is as high as 60 ° C. or higher, and in order to use such high-temperature exhaust heat directly as heating, the installation environment of the compressor is adjusted to an appropriate temperature by the high-temperature exhaust hot air. It is limited to a space that can sufficiently rise. That is, when the discharge destination space is narrower than the amount of discharged exhaust hot air, hot air cannot be directly discharged into the space. If this is used as heating heat by reducing it to an appropriate temperature, there remains a problem that the exhaust heat utilization efficiency is significantly reduced.
  • Patent Document 2 does not disclose controlling the amount of exhaust heat from the exhaust heat utilization side. That is, in Patent Document 2, for example, when more heat is required at the use destination of the exhaust hot air, it is necessary to operate the compressor that is the source of heat accordingly, but more exhaust hot air (thermal energy) is required. Increasing the operating energy of the compressor to produce is far from the idea of using exhaust heat. Similarly, when the operating energy of the compressor is not affected, it is not possible to flexibly meet the heat demand of the waste heat utilization destination. A technique that efficiently uses exhaust heat without affecting the operating efficiency of the compressor is desired.
  • a compressor comprising a compressor body, a drive source for driving the compressor, a heat exchanger for exchanging heat with the compressed gas discharged from the compressor body, and a fan device for generating cooling air flowing in the heat exchanger;
  • a compressor system having a heat exchange with the heat exchanger, and an exhaust passage through which exhausted air scavenged from the compressor flows, wherein the exhaust passage is branched into at least two,
  • the first branch path communicates with the first space and the second branch path communicates with a second space different from the first space, and at least one of the first branch path and the second branch path
  • the exhaust gas control device that circulates the cooling air through the exhaust air passage, the temperature sensor that detects the temperature of the first space, and the temperature of the compressed gas at a predetermined temperature by the fan device. Control to a predetermined temperature and based on the temperature detected by the temperature sensor , Compressor system and a control device for controlling the amount of exhaust air flowing through
  • exhaust heat can be used efficiently without affecting the operating efficiency of the compressor.
  • Other problems, configurations, and effects of the present invention will become apparent from the following description.
  • FIG. 1 is a block diagram schematically illustrating a configuration of a compressor according to Embodiment 1.
  • FIG. It is a flowchart which shows the process of the compressor system by Example 1.
  • FIG. It is a block diagram which shows typically the structure of the compressor system by Example 2 to which this invention is applied.
  • FIG. 1 schematically shows a configuration example of a gas compressor system 100 to which the present invention is applied.
  • the gas compressor system 1 includes a compressor 1, a duct 2 connected to a cooling air exhaust port of the compressor 1, and a plurality of exhaust hot air discharged through the exhaust port of the compressor 1 to the duct 2.
  • a fan device 3 and temperature sensors Ta, Tb, and Tc are provided.
  • the compressor 1 has a compressor main body 1 having a displacement type or turbo type compression mechanism, and compresses the sucked air or the like to discharge high-pressure compressed air.
  • the duct 2 includes a duct 2 a and a duct 2 b that are connected to the exhaust port of the compressor 1 on the upstream side and branch into a plurality on the downstream side.
  • the downstream outlet of the duct 2b communicates with another space (in this example, outdoors) different from the compression chamber A in which the compressor 1 is installed.
  • the downstream outlet of the duct 2a communicates with the compressor room A and another space different from the outside (in this example, a room B spatially partitioned from the compressor room A). That is, the chamber B is a space that can be said to communicate with the compressor 1 via the duct 2b, and the compression chamber A and the chamber B may be adjacent spaces as positions, or may be separated spaces. Good.
  • the ducts 2a and 2b have fan devices 3a and 3b for flowing exhaust hot air therein.
  • the fan devices 3a and 3b include turbo type or propeller type blades and an electric motor that rotationally drives the blades.
  • the fan devices 3a and 3b are connected to the control unit 30 of the compressor 1 via duct fan inverters 4a and 4b, and their driving is controlled.
  • the fan devices 3a and 3b are not limited to the rotary type fans, and the arrangement location is not limited to the inside of the ducts 2a and 2b, but may be arranged outside the outlet (outdoor side or room B side). Further, the fan devices 3a and 3b are not limited to rotary fans.
  • the temperature sensor Ta detects the temperature of the compressed air generated and discharged by the compressor 1. The detected value is used for various controls of the compressor 1.
  • the temperature sensor Tb is a temperature detection device that is disposed in the chamber B and detects the room temperature of the chamber B.
  • the temperature sensor Tb is connected to the control unit 30 or the like of the compressor 1 via a wired or wireless communication line, and transmits the detected temperature of the room B.
  • the temperature sensor Tc is a temperature detection device that is disposed in the compressor chamber A and detects the room temperature of the compressor chamber A.
  • the fan device 4 is a device that exhausts room air from the compressor chamber A to another space (in this example, the outside).
  • the gas in the other space flows into the compressor chamber A from the other space (in this example, the outside).
  • This inflow is caused by the compressor A becoming negative pressure due to the drive intake air of the compressor 1, but an unillustrated intake fan or the like is disposed so that the outside air flows into the compression chamber A from the outside. May be.
  • the compressor 1 compresses the sucked outside air by the compressor main body 12 and discharges it to the outside of the compressor 1 through a discharge pipe.
  • the exhaust hot air F ⁇ b> 1 is exhaust hot air that has undergone heat exchange with the discharged compressed air that has become hot due to compression through the heat exchanger and the fan device 10, and flows from the exhaust port of the compressor 1 to the duct 2 (F ⁇ b> 1, etc.).
  • the exhaust hot air F2 is exhaust heat air from the control unit 30 of the compressor 1 (or from the case where a dryer is installed), and from the exhaust port different from the exhaust port connected to the duct 2 to the outside of the compressor 1. It is the exhaust heat wind that is exhaled.
  • the exhaust hot air F2 is discharged to the outside together with a part of the outside air flowing into the compression chamber A from the outside by the fan device 4 that mainly exhausts the compressor chamber A.
  • the rotational speed of the fan device 4 is controlled based on the detected value of the temperature sensor Tc (including start / stop) so that the room temperature of the compressor room A becomes higher than the outdoor temperature that is the intake destination. It is supposed to be.
  • the control unit 30 controls the fan device 4 based on the detection value of the temperature sensor Tc.
  • FIG. 2 schematically shows the configuration of the compressor 1.
  • the compressor 1 is a screw compressor that supplies compressed oil to a compression working chamber to generate compressed air.
  • the compressor 1 is not limited to this.
  • a compressor that uses a gas other than air as the compression medium may be used, a liquid supply type that uses water or the like in addition to the lubricating oil, or a non-supply type that does not use liquid.
  • generates compressed air may be plural (a multistage structure is included).
  • the compressor 1 includes a compressor body 12 having a compression mechanism for compressing air, a main motor 11 as a drive source, a main motor inverter 31 that converts the power frequency of the main motor 11, a discharge pipe 15a through which discharged compressed air flows, 15b, 15c, a gas-liquid separator 21 arranged on these discharge piping systems, an air cooler 10, an oil cooler 18, a fan device 19 for generating cooling air to be supplied to these coolers, a control unit 30 for controlling the compressor 1, and A package housing 50 for storing these devices is mainly provided.
  • the control unit 30 is disposed on the discharge pipe 15 through which the compressed air discharged from the compressor body flows, and according to the detection value from the discharge temperature sensor Ta and the pressure sensor 25 that detects the temperature of the compressed air,
  • the main motor 11, the fan device 19, and the like are controlled so as to generate compressed air at a temperature and to control the efficient operation.
  • the discharge temperature sensor Ta can be installed in an arbitrary place of the discharge pipe 15.
  • the control unit 30 controls the operation of the fan device 19 (acceleration, deceleration, stop, etc.) or switches the switching valve via the fan inverter 20 according to the discharge temperature detected by the discharge temperature sensor Ta.
  • the amount of lubricating oil flowing into the oil cooler 18 is maintained in a predetermined temperature range.
  • control of the efficient operation performed by the control unit 30 for example, after starting, P, PI or PID control is performed based on the detection value of the pressure sensor 25 until the target pressure input and set in the control unit 30 is reached. This is control for controlling the rotational speed of the main motor 11 by changing the output frequency from the main motor inverter 31.
  • the main motor inverter It is possible to control the no-load operation for reducing the power by reducing the rotational speed of 31.
  • the no-load operation not only the rotation speed of the main motor 11 is reduced, but also the suction throttle valve 14 is “closed” to reduce the intake amount, and the air release valve 17 is “open” to release the compressed air from the discharge piping system. To do.
  • the control unit 30 performs load operation.
  • the load operation is an operation in which the pressure is increased again by setting the suction throttle valve 14 to “open” and / or the discharge valve to “close” in a state where the rotation speed of the main motor 11 is decreasing.
  • the control unit 30 switches to the no-load operation again.
  • control unit 30 repeats the no-load operation and the load operation to reduce the power of the compressor 1.
  • control unit 30 switches to operation by control such as PID.
  • control unit 30 is connected to the above-described temperature sensors Tb and Tc and the fan devices 3a and 3b via a wired or wireless communication line, and performs communication and control with these.
  • the temperature sensor Tb, the fan device 3a, and the like may be connected to and controlled by another control system other than the control unit 30.
  • a temperature sensor or a fan device is connected to a remote control device 65 via a wired / wireless communication line (network) 60, and can be communicated with the control device 65 or a wired / wireless communication line 61.
  • You may comprise so that it may control remotely by the input from the connected terminal 66 or the portable terminal 67.
  • the detection value of the discharge temperature sensor Ta may also be output to the control device 65 via the control unit 30.
  • the package housing 50 includes intake ports 40a and 40b for intake from the outside.
  • the intake port 40 a is an opening that mainly takes in outside air flowing into the drive system region such as the main motor 11 and the compressor main body 12, and the intake port 40 b is mainly in the region of the cooler system such as the air cooler 10 and the oil cooler 11. It is an opening for taking in outside air.
  • the package housing 50 includes, for example, exhaust ports 45a and 45b on the upper surface.
  • the exhaust port 45a is an exhaust port through which an airflow that is sucked from the intake port 40a and that cools the drive system such as the main motor 11 and the compressor body 12 is mainly exhausted.
  • the exhaust port 45 b is connected to the duct 2.
  • the exhaust port 45b is an exhaust port through which an airflow that is sucked from the intake port 40b and has cooled a cooler system such as the air cooler 10 is mainly exhausted.
  • the exhaust port 45a is not connected to the duct 2 and scavenges exhaust hot air into the compressor chamber A (see FIG. 1).
  • the control system such as the control unit 30 may be configured as an independent intake port that directly intakes air from outside, and may be scavenged from the exhaust port 45a. When a dryer is disposed, the intake / exhaust system thereof may be independent or may be partially used.
  • the airflow between the intake / exhaust ports 40a-45a and 40b-45b is mainly generated by driving the fan device 19 and the fan devices 3a and 3b. Further, when the main motor 11 is provided with a self-excited (or separately excited) fan, this can also be an element of airflow generation.
  • the operation of the compressor 1 thus configured is as follows.
  • the compressor main body 1 sucks outside air through an intake pipe 13a from an intake port 40a opened in a part of the package housing.
  • the sucked air flows into the intake portion of the compressor body through the air filter 13b, and flows into the compression working chamber through the suction throttle valve 14 that controls the intake amount.
  • the compressor main body 1 is a compression working chamber formed by the tooth space of the screw rotor and the bore wall surface of the compression main body, and compresses air by reducing the volume of the working chamber together with the supplied lubricating oil.
  • High-temperature (for example, about 110 ° C.) mixed compressed air is discharged to the discharge pipe 15a.
  • the discharge pipe 15a is connected to a centrifugal or collision type gas-liquid separator 21, in which the mixed compressed air is separated into air and lubricating oil.
  • the separated compressed air flows into the discharge pipe 15b through the pressure regulating check valve.
  • the lubricating oil separated by the gas-liquid separator 21 flows to the oil cooler 18 constituted by a heat exchanger via the lubricating oil pipe 16a.
  • the discharge pipe 15b is connected to the air cooler 10 composed of a heat exchanger, and the compressed air flowing from the gas-liquid separator 21 exchanges heat with the cooling air generated by the fan device 19 to obtain a desired temperature (for example, , About 70 ° C.) and is eventually supplied to the user side of the compressed air through the discharge pipe 15c.
  • a secondary filter that further removes oil may be disposed upstream of the air cooler 10.
  • the lubricating oil that has flowed from the lubricating oil pipe 16 a to the oil cooler 18 is cooled by cooling air and heat generated by the fan device 19 a.
  • the refrigerant is returned to the compressor body 12 through the lubricating oil pipe 16b and the oil filter 22.
  • the middle of the lubricating oil pipe 16a branches via a switching valve, one communicating with the oil cooler 18, and the other communicating directly with the lubricating oil pipe 16b.
  • the control unit 30 switches over the switching valve to prevent overcooling.
  • the output frequency of the inverter 21 is changed by a control command corresponding to the temperature of the mixed compressed air detected by the temperature sensor Ta by the control unit 30, and the final discharged compressed air temperature is set to a predetermined temperature (for example, , About 70 ° C.).
  • control of the temperature sensors Tb and Tc and the fan devices 3a and 3b by the control unit 30 will be described.
  • the control unit 30 usually operates the fan device 3b and scavenges all exhaust heat air flowing through the duct 2 from the duct 2b to the outside.
  • the exhaust hot air F1 of the compressor 1 is used for heating the B room, etc.
  • the operation of the fan device 3b that scavenges outdoors is limited (including deceleration and stop), and instead of the room B.
  • the fan device 3a is driven (including startup and acceleration) until the temperature sensor Tb disposed in the chamber B detects a predetermined temperature.
  • the predetermined temperature is, for example, a room temperature targeted by the room B (hereinafter, may be referred to as “B room set temperature”).
  • the room B set temperature can be arbitrarily set by the user using the input means.
  • a temperature setting device may be mounted as a controller in the B room together with the temperature sensor Tb, a temperature setting device may be mounted so as to be set from the control operation panel of the compressor 1, or the management device 65 or the terminal You may implement so that it can set remotely from 66.
  • the control unit 30 receives the detection signal of the room B set temperature from the temperature sensor Tb, the control of the fan device 3a is limited (including deceleration and stop), and instead, the fan device 3b is driven (starting and speeding up). (Including).
  • the specification is such that the maximum air volume of the fan device 19 of the compressor 1 and the maximum air volume of the fan device 3a or 3b of the duct 2 are at least equal to or greater. Furthermore, the sum of the air volume generated by the fan device 19 of the compressor 1 and the fan device 3a (and / or 3b) for the duct is more than an output that can secure at least an air volume sufficient for cooling the compressor 1. It is supposed to drive in.
  • the exhaust hot air F1 when the exhaust hot air F1 is not circulated through the duct 2a, in order to ensure the cooling performance of the compressor 1, it is necessary to exhaust all the exhaust hot air F1 of the fan device 19 to the outdoors by the fan device 3b. Is preferably set to be equal to or greater than the maximum air volume of the fan device 19. On the contrary, when the exhaust hot air F ⁇ b> 1 is circulated only through the duct 2 a, it is preferable that the maximum air volume of the fan device 3 a is set to be equal to or greater than the maximum air volume of the fan device 19. When the exhaust hot air F1 is dispersed in the ducts 2a and 2b, it is preferable that the sum of the blown air amounts of the fan devices 3a and 3b be equal to or greater than the swept air amount of the fan device 19.
  • the relationship between the air volumes generated by the fan devices 19, 3a, and 3b is preferably the following [Equation 1].
  • a processing flow of the compressor system 100 having the above configuration will be described with reference to FIG.
  • the following processing is executed by the control unit 30 in cooperation with the program and the arithmetic device.
  • control unit 30 controls the rotational speed of the electric motor 11 based on PID control in S103, and generates compressed air having a preset target discharge pressure.
  • the control unit 30 compares the detected temperature of the discharge temperature sensor Ta with the threshold temperature, and if the detected temperature exceeds the threshold (S105: Y), the fan device 19 and the fan device 3b are driven.
  • the number of rotations of the fan device is controlled according to the discharge temperature. For example, when the detected temperature of the discharge temperature sensor Ta is 110 ° C., the control unit 30 causes the air cooler 10 and the oil cooler 18 so that the compressed air temperature supplied to the user side of the compressed air becomes about 70 ° C. Controls the amount of cooling air to exchange heat with.
  • the rotation of the fan devices 19 and 3b is stopped (S115).
  • the control unit 30 checks whether the exhaust heat utilization setting set in the memory of the control unit 30 is ON or OFF. If it is ON (S107: Y), the process proceeds to S109, and if it is OFF Advances to (S107: N). When the exhaust heat utilization setting is OFF, all the cooling air (exhaust heat air) discharged from the compressor 1 through the duct 2 is discharged to the outdoors from the duct 2b.
  • the control unit 30 checks whether the temperature detected by the temperature sensor Tb in the room B is equal to or higher than the room B set temperature. If the detected temperature is equal to or higher than the room B set temperature (S109: Y), the process proceeds to S111. If the temperature is lower than the room B set temperature (S109: N), the process proceeds to S113.
  • the control unit 30 determines the number of rotations of the fan device 3a and the fan device 3b according to the difference between the detected temperature of the temperature sensor Tb of the chamber B and the set temperature of the chamber B, and becomes the number of rotations.
  • the drive of the fan device 3a is started, and the drive of the fan device 3b is limited.
  • the control unit 30 sets the rotation speed of the fan device 3a to the maximum rotation and stops the rotation of the fan device 3b.
  • all the exhaust hot air discharged from the compressor 1 to the duct 2 is caused to flow to the duct 2a.
  • the amount of exhaust heat air flowing through the duct 2a is determined by PID control according to the difference between the detection value of the temperature sensor Tb and the set temperature of the B room, so that if the difference is large, the fan devices 2a and 2b If the fan device 2a has a high rotational speed ratio and the difference is small, the rotational speed ratio of the fan device 2b becomes high. In some cases, the rotation speed ratio is the same.
  • the control unit 30 decreases the rotation speed of the fan device 3a (including stoppage), and conversely, the fan device 3b.
  • the rotation speed is increased (including start-up).
  • the sum of the air volumes generated by the fan devices 2a and 2b is equal to or greater than the air volume generated by the fan device 19.
  • the control unit 30 executes the process of S111 or S113 and then returns to S105 again to check the rotational speed of the fan device 19, and then sequentially executes the above-described processes. Therefore, the cooling performance of the compressor 1 is not affected, and the heat energy of the exhaust hot air can be used efficiently.
  • the first embodiment it is possible to dynamically control the amount of exhausted hot air used by the compressor 1. Furthermore, it is possible to efficiently use thermal energy without affecting the cooling performance of the compressor 1.
  • the balance of the air volume generated by the fan devices 3a and 3b is changed according to the detected temperature value of the B room.
  • Thermal energy can be used flexibly. For example, when the cooling demand of the compressor 1 decreases and the air volume generated by the fan device 19 is small, all the exhaust hot air in the duct 2a circulates to the B room side. Tends to be relatively maintained.
  • cooling air for cooling the compressor 1 is generated by a plurality of fan devices including the fan device 19 and the fan device 3a (and / or 3b). Therefore, the output and size of the fan device 19 mounted on the compressor 1 can be reduced. Reduction in power of the fan device 19 can be expected for a decrease in output, and downsizing of the compressor 1 can be expected for a reduction in size.
  • Example 1 was demonstrated, this invention is not limited to the said various structure and operation
  • the first embodiment has been described on the assumption that the air volumes generated by the fan devices 19, 3 a, and 3 b are equal, a combination of different maximum air volumes generated may be used.
  • a combination in which the maximum air volume of the fan device 3b is smaller than the maximum air volume of the fan device 3a is also possible.
  • the maximum amount of exhaust heat air required at the maximum on the use side of the exhaust heat air (for example, the space volume of the room B) may not be required.
  • the fan device 19 is variable speed by inverter control, but may be a constant speed fan device. This is because an efficient use effect of the exhaust hot air can be expected by the variable speed control of the fan devices 3a and 3b. Furthermore, it is possible to expect the above-mentioned effect by combining the fan device 19 with a variable speed and the fan device 3a or 3b with a variable speed.
  • the fan devices 2a and 2b have been described as PID control according to the temperature detected by the temperature sensor Tb. However, ON / OFF control based on the set temperature is also possible.
  • the duct 2 is branched into two, and one of the discharge destinations is outdoor and the other is indoor.
  • the number of branching of the duct is not limited to this, and both of the discharge destinations are indoors. There may be.
  • the discharge destination of the duct 2b is not necessarily indoor, and the duct 2b may pass through the B room, the discharge destination may be outdoor, and heat may be used in the B room as radiant heat of the duct 2b itself. .
  • Example 1 was the structure which controls the amount of exhaust heat air which flows through the ducts 2a and 2b which are each branch path of the duct 2 with the fan apparatuses 3a and 3b.
  • the second embodiment is different from the first embodiment in that a fan device controls the amount of exhaust heat airflow in one branch path, and that a dedicated fan device is not used to control the amount of exhaust heat airflow in another branch path.
  • the second embodiment is different from the first embodiment in that one or both of the branch paths are provided with a control device (shielding plate 7) that makes the opening degree of the flow path variable.
  • FIG. 4 schematically shows the configuration of the compressor system 200 according to the second embodiment.
  • FIG. 4 (a) shows that a dedicated fan device 3a for controlling the exhaust heat flow rate of the duct 2a communicating with the B room is not provided, and a dedicated fan device for controlling the exhaust heat flow rate of the duct 2b communicating with the outside is not arranged. It is the structure to arrange.
  • the shielding plate 7 is disposed in the duct 2b as a control device that controls the opening degree of the flow path in the duct and can control the amount of exhausted hot air flowing.
  • the shielding plate 7 includes an electric drive device (such as a motor or a solenoid) (not shown), and is configured to change the opening of the duct 2b flow path by making the tilt angle adjustable.
  • the opening degree of the shielding plate 7 is dynamically controlled by the control unit 30 of the compressor 1 (or the control device 65 that enables external communication). For example, when all the exhaust hot air in the duct 2 is circulated to the B room side, the shielding plate 7 is fully closed. On the other hand, when discharging all outdoors, the shielding plate 7 is fully opened.
  • the opening degree of the shielding board 7 shall be 50%.
  • the relationship between the flow rate of the duct 2b and the opening is a design value determined by the duct diameter, the duct length, the air volume of the fan device 3a, and the like.
  • FIG. 4B conversely to FIG. 4A, a configuration example in which the shielding plate 7 is disposed in the duct 2a communicating with the B room side and the fan device 3b is disposed on the duct 2b side communicating with the outdoors. It is.
  • the fan device 3b and the shielding plate 7 are operated in reverse to the relationship between the fan device 3a and the shielding plate 7 in FIG.
  • the second embodiment it is possible to reduce the number of dedicated fan devices (3a or 3b) that mainly control the exhaust heat flow rate of the duct 2.
  • the opening degree of the shielding plate 7 is a dynamic configuration using a driving device, but it can also be a separately excited type that is tilted by the wind of exhaust heat air in the duct.
  • the structure which applies the shielding board 7 to the duct 2a, 2b of Example 1, or both is naturally possible.
  • the fan devices 3a and 3b may be set at a constant speed, and the exhaust hot air flow rate of the ducts 2a and 2b may be controlled by adjusting the opening degree by the shielding plate 7.
  • Pressure sensor 30 ... Control part, 31 ... Main motor inverter, 40a, 40b ... Intake port, 45a, 45b ... exhaust port, 50 ... package housing, 60/61 ... network, 65 ... control device, 66 ... terminal, 67 ... portable terminal, 100/200 ... compressor system, A ... compressor room, B ... B room, Ta ... discharge temperature sensor, Tb / Tc ... temperature sensor, F1 / F2 ... exhaust hot air

Abstract

L'invention a pour but d'utiliser efficacement le rejet thermique sans affecter l'efficacité de fonctionnement d'un compresseur. L'invention concerne un système de compresseur comprenant les éléments suivants : un compresseur comprenant un corps de compresseur, une source d'entraînement pour entraîner le corps de compresseur, un échangeur thermique qui échange de la chaleur avec de l'air comprimé évacué par le corps de compresseur, et un dispositif de ventilateur qui génère de l'air de refroidissement qui s'écoule vers l'échangeur thermique ; et un passage d'échappement à travers lequel s'écoule l'échappement qui a échangé de la chaleur avec l'échangeur thermique et qui a été balayé vers l'extérieur du compresseur. Le passage d'échappement se ramifie en au moins deux passages, un premier passage ramifié étant relié à un premier espace, et un second passage ramifié étant relié à un second espace différent du premier espace. Le système de compresseur est pourvu des éléments suivants : un dispositif de commande d'échappement qui est disposé dans au moins l'un parmi le premier passage ramifié et le second passage ramifié, et amène l'air de refroidissement à s'écouler dans le passage d'échappement ; un capteur de température qui détecte la température du premier espace ; et un dispositif de commande qui commande la température de l'air comprimé par un dispositif de ventilateur de façon à être une température prescrite, et commande la quantité d'échappement traversant le premier passage ramifié par le dispositif de commande d'échappement sur la base de la température détectée par le capteur de température.
PCT/JP2018/002843 2017-04-24 2018-01-30 Système de compresseur WO2018198459A1 (fr)

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CN109708219A (zh) * 2018-12-18 2019-05-03 海信（广东）空调有限公司 一种除湿机
JP2020133420A (ja) * 2019-02-13 2020-08-31 山正機械株式会社 空調アダプター
JP7106691B1 (ja) 2021-01-19 2022-07-26 株式会社日立産機システム 流体機械システム

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KR102276103B1 (ko) * 2021-03-08 2021-07-12 한국에어로(주) 필터 청소기능과 난방 기능을 갖는 공기 압축 시스템
KR102420570B1 (ko) * 2021-10-27 2022-07-13 김수형 컴프레셔 발생 열 순환 시스템

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WO2012026317A1 (fr) * 2010-08-27 2012-03-01 株式会社日立産機システム Compresseur de gaz refroidi par huile
WO2016031985A1 (fr) * 2014-08-29 2016-03-03 ナブテスコオートモーティブ 株式会社 Séparateur d'huile et système de séchage à air comprimé

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JPS5123840A (ja) * 1974-08-23 1976-02-26 Hitachi Ltd Reidanboki
JPS5818082U (ja) * 1981-07-29 1983-02-03 株式会社日立製作所 空冷式パツケ−ジ圧縮機
WO2012026317A1 (fr) * 2010-08-27 2012-03-01 株式会社日立産機システム Compresseur de gaz refroidi par huile
WO2016031985A1 (fr) * 2014-08-29 2016-03-03 ナブテスコオートモーティブ 株式会社 Séparateur d'huile et système de séchage à air comprimé

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Publication number Priority date Publication date Assignee Title
CN109708219A (zh) * 2018-12-18 2019-05-03 海信（广东）空调有限公司 一种除湿机
CN109708219B (zh) * 2018-12-18 2021-02-02 海信（广东）空调有限公司 一种除湿机
JP2020133420A (ja) * 2019-02-13 2020-08-31 山正機械株式会社 空調アダプター
JP7112737B2 (ja) 2019-02-13 2022-08-04 山正機械株式会社 空調アダプター
JP7106691B1 (ja) 2021-01-19 2022-07-26 株式会社日立産機システム 流体機械システム
JP2022112530A (ja) * 2021-01-19 2022-08-03 株式会社日立産機システム 流体機械システム

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