WO2020195532A1 - 圧縮機 - Google Patents

圧縮機 Download PDF

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Publication number
WO2020195532A1
WO2020195532A1 PCT/JP2020/008218 JP2020008218W WO2020195532A1 WO 2020195532 A1 WO2020195532 A1 WO 2020195532A1 JP 2020008218 W JP2020008218 W JP 2020008218W WO 2020195532 A1 WO2020195532 A1 WO 2020195532A1
Authority
WO
WIPO (PCT)
Prior art keywords
compressor
branch pipe
compressed gas
main body
air
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/JP2020/008218
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
勇次 池村
智夫 鈴木
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 JP2021508861A priority Critical patent/JP7203201B2/ja
Publication of WO2020195532A1 publication Critical patent/WO2020195532A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F04B41/00—Pumping installations or systems specially adapted for elastic fluids
    • F04B41/02—Pumping installations or systems specially adapted for elastic fluids having reservoirs
    • 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
    • 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
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the present invention relates to a compressor and relates to a compressor that utilizes the adiabatic expansion of a compressed gas for cooling.
  • a compressor that compresses a gas such as air is equipped with a drive source such as an electric motor for driving the compressor body and a control system that controls each component inside the compressor.
  • the control system includes control components such as an arithmetic circuit, various switches, a transformer, a capacitor, and a reactor. Further, in the case of a variable speed machine controlled by an inverter, a circuit such as an inverter control system is provided.
  • control systems are generally stored in a control room of a semi-enclosed housing such as an electric box. That is, since it is a precision part, it is preferable to separate it from the machine room for dust prevention and the like.
  • the control system of the compressor also needs cooling. Therefore, various cooling structures and methods are known. For example, there are compressors equipped with a dedicated fan that introduces cooling air from the outside into the control room, and those that share the fan air of other devices.
  • Patent Document 1 is a compressor provided with an electric box for storing a control panel, and provided with cooling fins exposed to the outside from the electric box on the back surface side of the control panel.
  • Patent Document 1 is a technology that uses fan wind, and does not give sufficient consideration to cooling the control system of a compressor that is efficient and has a degree of freedom in selecting specifications.
  • An object of the present invention is to efficiently cool the control system of a compressor while providing a degree of freedom in selecting specifications.
  • a preferred example of the present invention is a drive source, a compressor body to which power is supplied by the drive source, a discharge piping system for circulating compressed gas discharged from the compressor body, and a control device for controlling the drive source.
  • a housing that houses the control device and has a region lower than the compressed gas that flows through the discharge piping system, and a housing that is branched from the discharge piping system and that allows the compressed gas to flow inside. It is a compressor equipped with a branch pipe that communicates with the body.
  • FIG. 1 It is a perspective view which shows typically the compressor in Example 1.
  • FIG. It is a system diagram of the compressor in Example 1. It is a figure which showed typically the control room in Example 1.
  • FIG. It is a figure which showed typically the inverter chamber in Example 1.
  • FIG. It is a figure which shows the control flow of the control apparatus in Example 1.
  • FIG. 1 is a perspective view schematically showing a multi-stage screw type compressor 1 (hereinafter, may be simply referred to as “compressor 1”) according to the first embodiment.
  • the compressor 1 is a multi-stage compressor that sucks air (atmosphere) as a compression medium and discharges compressed air. Note that this embodiment is not limited to the multi-stage type, screw type, and compressor that generates compressed air, but can be applied to various types of compressors.
  • the compressor 1 has an electric motor 10, a gear case 11, a control chamber 9, a low-pressure stage compressor main body 12, an intercooler 13, a high-pressure stage compressor main body 14, an aftercooler 15, and an inverter chamber 19 on a base 5. Etc., and have a configuration in which these are stored by the housing 6.
  • the electric motor 10 is a drive source for driving the low-pressure stage compressor main body 12 and the high-pressure stage compressor main body 14.
  • the inverter stored in the inverter chamber 19 controls the rotation speed of the electric motor 10 by controlling the frequency of the electric power supplied to the electric motor 10.
  • the electric motor 10 is used as the drive source, but other drive means using natural energy such as an internal combustion engine, a steam engine, and wind power can also be applied.
  • the gear case 11 includes a gear that transmits the driving force of the electric motor 10 to the low-pressure stage compressor main body 12 and the high-pressure stage compressor main body 14.
  • the gear case 11 is arranged between the electric motor 10 and the low-pressure stage compressor main body 12 and the high-pressure stage compressor main body 14.
  • the gear case 11 has a function of supporting the electric motor 10, the low-pressure stage compressor main body 12, and the high-pressure stage compressor main body 14 to form an integral structure.
  • the load side output shaft of the electric motor 10 is provided with a bull gear, and the compression of both compressor bodies is performed by meshing with the respective gears arranged on the drive shafts of the low pressure stage compressor main body 12 and the high pressure stage compressor main body 14. It is designed to drive a mechanism (for example, a screw rotor). Although described in the example of connection with gears, a belt suspension type or a shaft direct connection configuration may be used.
  • the low-pressure stage compressor body 12 is a liquid-free type screw compressor, and is provided with a positive displacement twin screw rotor type compression mechanism that compresses air by meshing the tooth grooves of male and female rotors.
  • the compression mechanism is not limited to the positive displacement twin screw rotor type, and if it is a screw type, it is a single screw type consisting of a gate rotor and a screw rotor, or a multi type consisting of meshing of three or more screw rotors. Etc. Various formats can be used.
  • the low-pressure stage compressor main body 12 sucks in air from the suction port and discharges the primary compressed compressed air to the intercooler 13.
  • the intercooler 13 is a heat exchanger that cools the compressed air of the primary compression discharged from the low-pressure stage compressor main body 12.
  • the intercooler 13 is arranged below the low-pressure stage compressor main body 12 and the high-pressure stage compressor main body 14 so as to extend over them.
  • the intercooler 13 exchanges heat between the coolant supplied from the outside of the compressor 1 (in this example, water, but another cooling medium may be used) via the water supply port 20a and the first-compressed compressed air. Is performed, and intermediate cooling of compressed air is performed. The intermediate-cooled compressed air flows to the suction side of the high-pressure stage compressor main body 14 via the intermediate discharge pipe 17.
  • the coolant supplied from the outside of the compressor 1 in this example, water, but another cooling medium may be used
  • the high-pressure stage compressor main body 14 applies the liquid-free twin screw compressor type as in the low-pressure stage compressor main body 12. It should be noted that other types can be applied in the same manner as the low pressure stage compressor main body 12.
  • the high-pressure stage compressor main body 14 sucks in the compressed air that is primarily compressed by the low-pressure stage compressor main body 12, and then discharges the high-pressure secondary compressed air that is further boosted.
  • the exhaled secondary compressed air flows to the aftercooler 15.
  • the aftercooler 15 is a heat exchanger that cools the secondary compressed air discharged from the high-pressure stage compressor main body 14. Like the intercooler 13, the aftercooler 15 is arranged below the low-pressure stage compressor main body 12 and the high-pressure stage compressor main body 14 so as to extend across the low-pressure stage compressor main body 12 and the high-pressure stage compressor main body 14. To do. Further, the aftercooler 15 is arranged closer to the right side surface of the compressor 1 than the intercooler 13.
  • the aftercooler 15 exchanges heat between the coolant supplied from the outside of the compressor 1 and the second-compressed compressed air via the water supply port 20a to perform secondary cooling of the compressed air. There is.
  • the secondarily cooled compressed air flows to the outside of the compressor 1 (user-side piping system, etc.) through the discharge port 18 of the aftercooler 15.
  • an air-cooled type can also be used as the cooling means for the compressed gas.
  • the housing 6 surrounds the electric motor 10, the gear case 11, the low-pressure stage compressor main body 12, the intercooler 13, the high-pressure stage compressor main body 14, the aftercooler 15, the control room 9, the inverter room 19, etc. from the front, side, back, and top surfaces. It consists of a panel. An external suction port 7 for sucking air from the outside is arranged on the upper surface of the housing 6.
  • the intake duct 4 is arranged in the machine room 25 between the external suction port 7 and the suction port of the low-pressure compressor main body 12. Further, in this embodiment, the inverter chamber 19 and the machine room 25 for storing the electric motor, the compressor main body, the intercooler 13, the aftercooler 15, and the like are partitioned by the internal partition wall 8.
  • control room 9 is a communication for controlling wired or wireless communication with the user I / F unit 30 that visually, auditorily, and tactilely outputs information related to input and operation of various driving operations of the compressor 1. It includes a control device and an operation control device having a control board A60, a control board B61, a switch 66, and the like, which will be described later. It has a housing 9a for storing these control devices and the like inside.
  • the inverter room 19 includes a power conversion device (inverter 70 described later) that controls the frequency of the power supplied to the electric motor 10 based on a command from the control device of the control room 9.
  • a power conversion device inverter 70 described later
  • the control device may have, for example, a configuration in which a functional unit is realized by cooperation between an arithmetic unit and a program, or a part or all of the control device may have an analog circuit configuration.
  • the user I / F unit 30 may be a stationary type that is fixedly installed on the compressor 1, or may be a portable type such as a portable device.
  • various arithmetic units and resistors stored in the control room 9, power conversion devices and capacitors stored in the inverter room 19 are heating elements, and therefore require cooling.
  • some of these coolings are forced cooling by a cooling fan or the like, but a cooling device having a rating commensurate with the amount of heat generated is required.
  • the cooling performance of forced cooling depends on the temperature of the ambient environment in which the compressor 1 is installed, a size and energy considering this are also required.
  • the panel of the housing 6 is composed of one or a plurality of divided panels on each surface.
  • the inside of the compressor 1 is not visually open to the outside for equipment maintenance and soundproofing, except for some openings for intake and exhaust. Therefore, the housing 6 has a semi-sealed structure. Therefore, the machine room 25 of the compressor 1 tends to become hot due to the heat generated by the electric motor 10, the low-pressure stage compressor main body 12, the high-pressure stage compressor main body 14, and the like, and the control room 9 is also affected by this heat. Become.
  • the heat of the power converter or the like also contributes to the increase in the internal space temperature of the compressor 1.
  • the power conversion device and the like in the inverter chamber 19 are also affected by the heat in the machine room 25. It is also necessary to consider these points in the forced cooling means of the control chamber 9 and the inverter chamber 19.
  • one of the features is that the compressed air generated by the compressor 1 is adiabatically expanded and used for cooling the control chamber 9 and the inverter chamber 19.
  • the compressor 1 includes branch pipes 41a, 41b, 41c, and 41d, and the compressor air is diverted from the discharge pipe system by these branch pipes, and adiabatic expansion is performed inside the control chamber 9 and the inverter chamber 19.
  • the cooling effect due to adiabatic expansion is obtained by allowing air to be released under atmospheric pressure lower than that of the compressed gas.
  • the discharge piping system is a set of discharge piping that circulates compressed air supplied from the compressor body to the user side via a heat exchanger.
  • control room 9 and the inverter room 19 may be referred to as a "control system”.
  • FIG. 2 is a system diagram of the device, piping, and control in the compressor 1 of the first embodiment.
  • solid arrows indicate air and cooling water piping systems
  • dotted arrows indicate control systems.
  • the operation control device of the control chamber 9 is arranged in the temperature sensor 50a, the pressure sensor 51a and the temperature sensor 50b arranged in the discharge pipe extending from the low pressure stage compressor main body 12, and in the discharge pipe extending from the high pressure stage compressor main body 14. Receives temperature and pressure inputs from the temperature sensor 50c and pressure sensor 51b. Then, the operation control device outputs a frequency command to the power conversion device of the inverter chamber 19 so as to have a predetermined discharge pressure.
  • the power conversion device controls the rotation speed of the electric motor 10 by controlling the frequency of the electric power supplied to the electric motor 10 in response to the frequency command.
  • the compressor 1 includes branch pipes 41a, 41b, 41c, 41d in the discharge pipe system.
  • the branch pipe 41a is a main pipe through which compressed air to be adiabatically expanded is circulated.
  • the branch pipe 41b branches from the discharge pipe system downstream of the intercooler 13 and upstream of the high-pressure stage compressor main body 14 and is connected to the branch pipe 41a.
  • the branch pipe 41c branches from the discharge pipe system downstream of the aftercooler 15 and upstream of the air tank 90 (downstream of the discharge port 18 in this example), and is connected to the branch pipe 41a.
  • the branch pipe 41d branches from the air tank 90 outside the compressor 1 or the pipe (not shown) on the compressed air user side downstream of the air tank 90, and is connected to the branch pipe 41a via the branch pipe inlet 40 and the valve 43d. When branching from the air tank 90, compressed air can be supplied even when the compressor main body is stopped.
  • the branch pipe 41a that joins and connects with the three branch pipes 41b, 41c, 41d is adapted to connect the outlet side to the branch pipe inlets 42a, 42b of the control room 9 and the inverter room 19, which will be described later.
  • branch pipes 41b, 41c, 41d branch from the downstream of the heat exchanger that cools the compressed air such as the intercooler 13 and the aftercooler 15. That is, the present embodiment is not limited, but in the present embodiment, when the object to be cooled by the adiabatic expanded air is an electric / electrical device, the dehumidified and drier and cooled air enjoys the merit of maintenance. it can.
  • the branch pipes 41a, 41c, 41d are provided with solenoid valves that allow / restrict the flow of air. These solenoid valves are provided with valves 43a, 43b, 43c, 43d. The valve may be opened and closed in two stages or may be controlled in multiple stages.
  • valves 43a, 43b, 43c, 43d are designed to allow / restrict the flow of air by a command from the control device of the control room 9. Further, the operation of each valve 43a, 43b, 43c, 43d is also arbitrary. For example, control is performed such as limiting the valve 43d and permitting the valves 43a and 43c.
  • the branch pipe 41a branches on the downstream side, and one is connected to the branch pipe lead-in port 42a of the control chamber 9 and the other is connected to the branch pipe lead-in port 42b of the inverter chamber 19 via an orifice 44, respectively.
  • the orifice 44 is a valve body that permits / restricts the flow of air according to the pressure of the branch pipe 41a. This is to limit the amount of diffused air to a predetermined range from the viewpoint of cooling degree and maintenance of the control system. As the orifice 44, either a mechanical type or an electric type can be applied.
  • the solenoid valve is applied to the valves 43a, 43b, 43c, and 43d, but the present invention is not limited to this, and a manual valve and a mixed loading of the manual valve and the solenoid valve are applied. You can also do it.
  • the diameter of the branch pipe will be described as being smaller than the diameter of the discharge pipe, but the diameter is not limited to this, and the diameter is the same or larger in terms of the desired amount of compressed air and maintenance. Is optional.
  • the diameter of the branch pipe By making the diameter of the branch pipe smaller than the diameter of the discharge pipe, it is possible to prevent the amount of compressed air provided to the user or the like from being excessively reduced. Further, the same effect can be achieved by adjusting the flow of compressed air with the valves 43a, 43b, 43c, 43d and the orifice 44 without limiting the relationship between the diameters of the pipes.
  • FIG. 3 is a diagram schematically showing the control chamber 9 in the first embodiment.
  • the left side shows the front view of the control chamber 9
  • the right side shows the right side view (some parts are transparently shown).
  • the control room 9 mainly includes a control board A60, a control board B61, a transformer 62 for changing the voltage between these control boards, a relay 63, a power supply device 64, circuit breakers 65a and 65b, a switch 66, and a user I / F unit 30. , And these are stored in the housing 9a.
  • the housing 9a has a structure that is visually sealed to prevent the intrusion of dust and the like, but has a semi-sealed structure that has a gap that slightly allows the flow of gas.
  • one or a plurality of wiring lead-in ports 67 for taking in various wirings are arranged below the right side surface, and a branch pipe lead-in port 42a communicating with the branch pipe 41a is arranged above the wiring lead-in ports 67. ..
  • the position of the branch pipe lead-in port 42a is arbitrary, but it is preferable to arrange the control component that requires more cooling so that sufficient adiabatic expanded air is applied to the control component.
  • the control board A60, the control board B61, and the like including the arithmetic unit are arranged in the main diffusion direction of the adiabatic expanded air.
  • each control component of the control chamber 9 can be cooled. Further, since the adiabatic expanded air diffuses inside the housing 9a, the pressure becomes relatively high with respect to the outside. Therefore, it can be expected to have the effect of further preventing the intrusion of dust and the like into the control system having many precision parts.
  • the housing 9a has a configuration in which an adiabatic expanded air exhaust port is not particularly arranged, but the present invention is not limited to this.
  • FIG. 4 is a diagram schematically showing the inverter chamber 19 in the first embodiment.
  • the left side shows the left side surface of the inverter chamber 19
  • the right side shows the front view (the front view on the right side shows the inverter 70 transparently by omitting some parts).
  • the inverter chamber 19 includes an inverter 70 as control system components, a reactor 72 which is a passive element, an inverter 70, and other control components 74, which are housed by a housing 6 and an internal partition wall 8. Further, a duct 80 is arranged by a partition wall on the back surface side of the inverter 70 (the left side of the inverter 70 on the left side of FIG. 4 and the back side of the inverter 70 on the right side of FIG. 4). Below the duct 80, a branch pipe inlet 42b that takes in compressed air from the branch pipe 41a is arranged below the duct 80. An exhaust port 76 is arranged above the duct 80, and a fan 75 is arranged on the downstream side in the duct of the exhaust port 76.
  • a heat dissipation fin 71 is arranged inside the duct 80 on the back surface of the inverter 70.
  • the inverter 70 requires cooling of the power element (IGBT) which is a high heating element, a duct 80, a heat radiation fin, and a fan 75 are arranged on the back surface side to perform forced air cooling. It has become.
  • IGBT power element
  • the adiabatic and expanded air diffused from the branch pipe inlet 42b to the duct 80 is discharged to the outside from the exhaust port 76 after cooling the heat radiation fins 71 and the like. From the above configuration, the inverter chamber 19 can be cooled.
  • adiabatic expanded air is used especially for cooling the inverter 70 .
  • the present invention is not limited to the above embodiment, and the duct 80 is not arranged and the adiabatic expanded air is diffused throughout the inside of the inverter chamber 19, and the reactor 72, the circuit breaker 73, and other control parts are also cooled. You may try to do it.
  • the duct 80 may be configured to diffuse the adiabatic expanded air to the other region.
  • the fan 75 is arranged, but the effect can be obtained without the fan 75.
  • valves 43a, 43b, 43c, 43d will be described.
  • the following control is executed by the control device of the control room 9.
  • all of the valves 43a, 43b, 43c, and 43d will be opened and closed at the same time.
  • FIG. 5 is a diagram showing a control flow of the control device according to the first embodiment.
  • the compressor 1 receives a command to start operation from the user I / F unit 30, and the control device starts operation of the compressor based on the target pressure input via the user I / F unit 30 (step S1). ).
  • the control device outputs a command to the solenoid valve and controls the valves 43a, 43b, 43c, and 43d to be "open". As a result, the adiabatic expanded air is diffused into the control chamber 9 and the inverter chamber 19, and cooling is started (step S2).
  • the control device receives an operation stop command or another stop command from the user I / F unit 30, outputs a stop command to the inverter chamber 19, stops the operation of the electric motor 10, and controls to stop the compressor. (Step S3).
  • the control device outputs a command to the solenoid valve and controls the valves 43a, 43b, 43c, and 43d to be "closed” (step S4).
  • control system can be cooled by the adiabatic expansion of compressed air. Also, when the forced cooling device of the control system is used together, the size of the forced cooling device can be reduced and energy can be saved.
  • branch pipes 41b, 41c, and 41d branch from the downstream side of the cooler, it is possible to provide dry adiabatic expanded air by the control system, and an effect on maintenance can be expected.
  • branch pipes 41b, 41c, and 41d are arranged, but the configuration may be such that only one or any two branch pipes are combined.
  • the above-described embodiment is configured to open and close each valve according to the drive of the compressor 1, it may be configured to open and close arbitrarily via the user I / F unit 30.
  • the cooling of the control system by adiabatic expansion can also be used for temporary cooling or emergency cooling.
  • the opening and closing of each valve may be controlled according to the temperature information of the control chamber 9 and the inverter chamber 19.
  • the compressor 1 has been described as a package type including the housing 6, but a configuration without this may be used. Further, although the control chamber 9 and the inverter chamber 19 also have a housing structure, the configuration may be such that there is no housing.
  • a multi-stage non-supply liquid type screw compressor is used, but a single stage type or a liquid supply (water or oil) type may be used, and not only the screw but also other volume type / centrifugal type It may be a type compressor.
  • the above-described embodiment is a water-cooled compressor
  • an air-cooled compressor may be used.
  • the adiabatic expanded air may be used for cooling the inverter that drives and controls the fan device.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
PCT/JP2020/008218 2019-03-27 2020-02-28 圧縮機 Ceased WO2020195532A1 (ja)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2021508861A JP7203201B2 (ja) 2019-03-27 2020-02-28 圧縮機

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Application Number Priority Date Filing Date Title
JP2019-060561 2019-03-27
JP2019060561 2019-03-27

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Publication Number Publication Date
WO2020195532A1 true WO2020195532A1 (ja) 2020-10-01

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113597199A (zh) * 2021-06-22 2021-11-02 上海市政工程设计研究总院（集团）有限公司 一种高压变频器散热的智能控制系统及控制方法

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06346875A (ja) * 1993-06-10 1994-12-20 Hitachi Ltd パッケージ形スクリュー圧縮機
JP2002332979A (ja) * 2001-05-10 2002-11-22 Kobe Steel Ltd パッケージ型注油式圧縮機
JP2017166401A (ja) * 2016-03-16 2017-09-21 株式会社日立産機システム 多段圧縮機
JP2018028407A (ja) * 2016-08-18 2018-02-22 三菱重工サーマルシステムズ株式会社 冷凍サイクル装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06346875A (ja) * 1993-06-10 1994-12-20 Hitachi Ltd パッケージ形スクリュー圧縮機
JP2002332979A (ja) * 2001-05-10 2002-11-22 Kobe Steel Ltd パッケージ型注油式圧縮機
JP2017166401A (ja) * 2016-03-16 2017-09-21 株式会社日立産機システム 多段圧縮機
JP2018028407A (ja) * 2016-08-18 2018-02-22 三菱重工サーマルシステムズ株式会社 冷凍サイクル装置

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113597199A (zh) * 2021-06-22 2021-11-02 上海市政工程设计研究总院（集团）有限公司 一种高压变频器散热的智能控制系统及控制方法

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JPWO2020195532A1 (https=) 2020-10-01

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