WO2018003748A1 - Réfrigérateur - Google Patents

Réfrigérateur Download PDF

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Publication number
WO2018003748A1
WO2018003748A1 PCT/JP2017/023420 JP2017023420W WO2018003748A1 WO 2018003748 A1 WO2018003748 A1 WO 2018003748A1 JP 2017023420 W JP2017023420 W JP 2017023420W WO 2018003748 A1 WO2018003748 A1 WO 2018003748A1
Authority
WO
WIPO (PCT)
Prior art keywords
lubricating oil
oil
oil tank
tank
refrigerant
Prior art date
Application number
PCT/JP2017/023420
Other languages
English (en)
Japanese (ja)
Inventor
直也 三吉
上田　憲治
長谷川　泰士
Original Assignee
三菱重工サーマルシステムズ株式会社
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 三菱重工サーマルシステムズ株式会社 filed Critical 三菱重工サーマルシステムズ株式会社
Priority to CN201780016599.XA priority Critical patent/CN108779946B/zh
Priority to US16/081,612 priority patent/US20190078811A1/en
Publication of WO2018003748A1 publication Critical patent/WO2018003748A1/fr

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Classifications

    • 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
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/06—Lubrication
    • F04D29/063—Lubrication specially adapted for elastic fluid pumps
    • 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
    • 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
    • F25B31/004—Lubrication oil recirculating arrangements
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F25B31/026—Compressor arrangements of motor-compressor units with compressor of rotary type
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/01—Heaters
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/16—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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21155—Temperatures of a compressor or the drive means therefor of the oil

Definitions

  • the present invention relates to a refrigerator.
  • the turbo compressor installed in the turbo refrigerator is composed of a compression mechanism, a speed increasing mechanism, and the like.
  • the lubricating oil system includes an oil tank and an oil pump, and the lubricating oil stored in the oil tank is supplied to the bearings and gears of the turbo compressor by the oil pump.
  • the lubricating oil supplied to the bearings and gears is returned to the oil tank and repeatedly circulates through the lubricating oil system.
  • the refrigerant system and the lubricating oil system are not completely independent, the refrigerant is dissolved in the lubricating oil. Since the viscosity of the lubricating oil decreases when the refrigerant dissolves, the inside of the oil tank is maintained at a low pressure in order to reduce the amount of refrigerant dissolved in the oil tank. Therefore, for example, a pressure equalizing pipe that communicates with a low-pressure portion (for example, an evaporator or a compressor suction port) of the refrigerant system is connected to the oil tank.
  • a low-pressure portion for example, an evaporator or a compressor suction port
  • Patent Document 1 since the pressure in the oil tank is reduced when the turbo chiller is started, and the refrigerant dissolved in the lubricating oil is gasified and formed, the refrigerant passing through the turbo compressor is started at the start.
  • Patent Document 2 discloses a technique for equalizing the oil tank internal pressure and the economizer internal pressure by connecting the other end of the pressure equalizing pipe whose one end is connected to the oil tank to an economizer instead of an evaporator. ing.
  • the internal pressure decreases at the start-up or transition of the turbo refrigerator where the pressure of the refrigerant system decreases.
  • the time of transition is when changing the operating state, for example, when lowering the output of the turbo chiller.
  • the oil level rises compared to the normal time when the forming phenomenon does not occur.
  • the amount of lubricating oil that can be supplied to bearings, gears, and the like in the lubricating oil system decreases.
  • a low-pressure refrigerant for example, R1233zd
  • a high-pressure refrigerant for example, R134a
  • the gas volume generated in the forming phenomenon is large. Therefore, in the low-pressure refrigerant, the difference from the normal time is further increased with respect to the increase in the oil level and the decrease in the amount of oil supply.
  • the pressure equalizing pipe connected to the oil tank is connected to the upper part of the oil tank.
  • the formed lubricating oil flows into the pressure equalizing pipe, and the lubricating oil is connected to the destination of the pressure equalizing pipe.
  • the oil pump on the bottom of the oil tank while increasing the depth of the oil tank so that the oil pump does not suck the refrigerant gas at the time of forming, the position of the oil surface and the oil pump at the time of forming is changed. They are also being released.
  • This invention is made
  • the refrigerator of the present invention employs the following means. That is, the refrigerator according to the present invention includes an electric compressor having a compression mechanism driven by a motor, a condenser, an evaporator, a refrigeration cycle in which refrigerant circulates, an oil tank in which lubricating oil is stored, A heater installed in the oil tank for heating the lubricating oil; and connected to the oil tank for supplying the lubricating oil from the oil tank to a housing for housing the motor; An oil circulation pipe for returning the lubricating oil to the tank, and one end connected to the oil tank separately from the oil circulation pipe, the other end is installed in the pressure equalization pipe connected to the refrigeration cycle, and the pressure equalization pipe, A buffer tank for receiving the refrigerant and the lubricating oil flowing out from the oil tank and storing the lubricating oil.
  • an electric compressor having a compression mechanism driven by a motor, a condenser, an evaporator, a refrigeration cycle in which refrigerant circulates, an oil tank in
  • the motor that drives the compression mechanism is housed in the housing, and the lubricating oil is supplied from the oil tank to the housing, so that the lubricating oil lubricates the bearings that support the rotating shaft of the motor.
  • the lubricating oil lubricates the bearings that support the rotating shaft of the motor.
  • one end of the pressure equalizing pipe is connected to the oil tank, and the other end of the pressure equalizing pipe is connected to the refrigeration cycle, so that the pressure at the connection portion with the refrigeration cycle is substantially equal to the pressure in the oil tank.
  • the part to which the pressure equalizing pipe is connected in the refrigeration cycle is a part where the pressure is low in the refrigeration cycle such as an evaporator and a compressor suction port.
  • the refrigerant and lubricating oil that have flowed out of the oil tank are supplied to the buffer tank via the pressure equalizing pipe, and are temporarily stored in the buffer tank.
  • the lubricating oil is stored in the buffer tank and does not flow to the refrigeration cycle, but only the refrigerant goes to the refrigeration cycle.
  • one end is connected to the buffer tank, and the other end is connected to the oil tank separately from the pressure equalizing pipe, and a return pipe for returning the lubricating oil stored in the buffer tank to the oil tank is further provided. You may prepare.
  • one end of the return pipe is connected to the buffer tank, and the other end of the return pipe is connected to the oil tank, so that the lubricating oil stored in the buffer tank is returned to the oil tank.
  • the lubricating oil that has flowed out of the oil tank and accumulated in the buffer tank is returned to the oil tank without flowing into the refrigerant cycle.
  • the position where the return pipe is connected to the oil tank may be close to the position where the oil circulation pipe is connected in the oil tank.
  • the lubricating oil returned from the buffer tank is returned to the vicinity of the position where the oil circulation pipe is connected in the oil tank, the lubricating oil returned from the buffer tank is formed in the oil tank 23. Even if it occurs, it is mixed with lubricating oil that is not affected by forming.
  • the oil tank may be divided by a partition plate into a separation region where the lubricating oil returned from the housing flows and a discharge region where the lubricating oil is supplied to the housing.
  • the lubricating oil in which the refrigerant is dissolved is supplied to the separation region, and the lubricating oil in which the refrigerant is dissolved in the separation region is separated into the lubricating oil and the refrigerant. Then, the separated lubricating oil is supplied from the separation region to the discharge region and is supplied into the housing. Since the separation region and the discharge region are partitioned by a partition plate, the lubricating oil flowing into the oil tank is efficiently separated in the separation region by utilizing the difference between the lubricating oil and the refrigerant and the closed space. . Further, even if the forming phenomenon occurs in the separation region, it is possible to prevent the foamed lubricating oil from flowing into the discharge region.
  • a flow forming plate for directing the flow of the lubricating oil stored in the oil tank from the upper part to the lower part or from the lower part to the upper part may be installed in the separation region.
  • the partition plate may be installed separately from the bottom surface of the oil tank.
  • the lubricating oil in which the refrigerant has melted flows downstream without staying at the bottom in the divided region.
  • turbo refrigerator 1 concerning one embodiment of the present invention is explained with reference to drawings.
  • the turbo refrigerator 1 includes a turbo compressor 2 that compresses the refrigerant, a condenser 3 that cools and condenses the refrigerant, and further cools and supercools the refrigerant condensed in the condenser 3.
  • a sub-cooler 4 that gives the refrigerant, a first pressure-reducing valve 5 that depressurizes the high-pressure refrigerant to an intermediate pressure, an intermediate cooler 6 that gives supercooling to the refrigerant, a second pressure-reducing valve 7 that depressurizes the refrigerant to low pressure, and a low-pressure refrigerant
  • An evaporator 8 for evaporating is provided.
  • the turbo compressor 2, the condenser 3, the subcooler 4, the first pressure reducing valve 5, the intermediate cooler 6, the second pressure reducing valve 7 and the evaporator 8 constitute a refrigeration cycle, and the refrigerant is the turbo compressor 2, the condenser. 3, the subcooler 4, the first pressure reducing valve 5, the intermediate cooler 6, the second pressure reducing valve 7, and the evaporator 8 are circulated in this order. Further, the refrigerant is supplied from the intercooler 6 to the turbo compressor 2 by bypass without passing through the evaporator 8.
  • the turbo compressor 2 includes a housing 30 configured by integrally connecting a motor housing 31, a speed increaser housing 32, and a compressor housing 33.
  • the motor housing 31 incorporates a motor 9 that is driven at a variable speed by an inverter device.
  • One end 10 a of the motor shaft 10 of the motor 9 protrudes from the motor housing 31 to the speed increaser housing 32.
  • the motor 9 includes a stator 20 and a rotor 21.
  • a rotor 21 is fixed to the motor shaft 10, and the rotor 21 rotates inside the stator 20.
  • the motor shaft 10 is supported by the rolling bearing 14 on the speed increaser housing 32 side.
  • the rolling bearing 14 is composed of, for example, a plurality of angular ball bearings.
  • the rolling bearing 14 is installed in the motor housing 31 via a bearing box (not shown).
  • the compressor housing 33 accommodates a compression mechanism 15 having a first stage compression stage and a second stage compression stage.
  • the refrigerant sucked into the first stage compression stage from the outside and compressed by the first stage compression stage is sent to the second stage compression stage. Then, the refrigerant sucked into the second stage compression stage and compressed by the second stage compression stage is discharged to the outside.
  • a rotary shaft 11 is rotatably installed in the compressor housing 33.
  • a first stage impeller 12 for the first stage compression stage and a second stage compression stage are disposed on one end 11a side of the rotary shaft 11.
  • the second stage impeller 13 is provided.
  • the rotating shaft 11 is supported by the rolling bearing 14 on the speed increaser housing 32 side.
  • the rolling bearing 14 is composed of, for example, a plurality of angular ball bearings.
  • the rolling bearing 14 is installed in the compressor housing 33 via a bearing box (not shown).
  • a small-diameter gear 17 is provided on the other end 11b side of the rotary shaft 11 supported by the rolling bearing 14.
  • the gear 17 is meshed with a large-diameter gear 18 provided at one end 10 a of the motor shaft 10, and a speed increasing mechanism 19 is configured by these gears 17 and 18.
  • the speed increasing mechanism 19 is accommodated in the speed increasing device housing 32.
  • Lubricating oil is supplied to the rolling bearing 14 and the gears 17 and 18 for each component.
  • the lubricating oil system includes a lubricating oil supply line 22 and a lubricating oil discharge line 25.
  • the lubricating oil supply line 22 is a pipe connecting the oil tank 23 and the turbo compressor 2.
  • the lubricating oil is supplied from the oil tank 23 to the motor housing 31 and the speed increaser housing 32 of the turbo compressor 2 by an oil pump 36 provided in the lubricating oil supply line 22.
  • the lubricating oil that has passed through the motor 9 and the speed increasing mechanism 19 is returned to the oil tank 23 via the lubricating oil discharge line 25.
  • An oil cooler 24 is installed in the lubricating oil supply line 22 and the lubricating oil discharge line 25 according to the present embodiment.
  • a lubricating oil inlet connected to the lubricating oil supply line 22 is formed, and the lubricating oil is supplied from the lubricating oil supply line 22 to the turbo compressor 2.
  • the turbo compressor 2 is supplied with the refrigerant extracted from the condenser 3 constituting the refrigeration cycle.
  • a liquid refrigerant inlet connected to the refrigerant supply line 34 is formed in the motor housing 31 and the speed increaser housing 32, and the liquid refrigerant is supplied from the refrigerant supply line 34.
  • the lubricating oil that has passed through the motor housing 31 and the speed increaser housing 32 of the turbo compressor 2 is discharged to the oil tank 23.
  • the motor housing 31 and the speed increaser housing 32 are formed with a lubricating oil outlet connected to the lubricating oil discharge line 25, and the motor housing 31 and the speed increaser housing 32 are connected to the oil tank 23 via the lubricating oil discharge line 25. Refrigerant and lubricating oil are discharged.
  • the lubricating oil discharged to the oil tank 23 has a refrigerant dissolved therein and diluted with the refrigerant.
  • the oil tank 23 is provided with a heater 27 (see FIG. 3) that evaporates the refrigerant in order to increase the concentration of the diluted lubricating oil. As the refrigerant evaporates, the lubricating oil returns to the state before dilution and can be repeatedly used as lubricating oil for lubricating the gears 17 and 18 and the rolling bearing 14.
  • the oil tank 23 is a container that can contain lubricating oil, and the lubricating oil is stored in a lower portion inside the oil tank 23.
  • the oil tank 23 can be roughly divided into a separation region 41 and a discharge region 42.
  • the oil tank 23 is formed with a lubricant / refrigerant inlet connected to the lubricant discharge line 25.
  • the heater 27 is installed, for example, below the separation region 41 of the oil tank 23, heats the refrigerant and lubricating oil in the oil tank 23, and evaporates the refrigerant.
  • the refrigerant gas generated by evaporation moves upward of the oil tank 23, and the lubricating oil having a reduced content of the refrigerant evaporated from the refrigerant flows downstream of the oil tank 23.
  • a lubricant outlet connected to the lubricant supply line 22 is formed below the oil tank 23.
  • an oil pump 36 is installed at the lubricating oil outlet. Lubricating oil is supplied from the oil tank 23 to the turbo compressor 2 via the lubricating oil supply line 22.
  • a refrigerant gas outlet connected to the pressure equalizing pipe 29 is formed above the oil tank 23, and the refrigerant gas is supplied from the oil tank 23 to the evaporator 8 through the pressure equalizing pipe 29.
  • coolant supplied to the turbo compressor 2 from the condenser 3 or the subcooler 4 is returned to a refrigerating cycle.
  • one end of a pressure equalizing pipe 29 is connected to the oil tank 23, and the other end of the pressure equalizing pipe 29 is connected to the evaporator 8 of the refrigeration cycle.
  • the pressure and the pressure in the oil tank 23 are almost equal.
  • the connection destination of the pressure equalizing pipe 29 is not limited to the evaporator 8 and may be, for example, the suction port of the turbo compressor 2.
  • the lubricating oil stored in the oil tank 23 is preferably adjusted so as to be maintained within a predetermined temperature range.
  • the temperature of the lubricating oil is determined based on, for example, the temperature at which appropriate lubrication is exerted in the gears 17 and 18 of the turbo compressor 2 and the rolling bearing 14 that are lubricated by the lubricating oil.
  • the temperature of the lubricating oil stored in the oil tank 23 is adjusted by heating with the heater 27, for example. Heating by the heater 27 is controlled based on the temperature detected by the temperature detection unit 35 installed in the lower part of the oil tank 23.
  • the heater 27 may be controlled to be turned on / off based on the detected temperature to adjust the heating to the refrigerant or the lubricating oil, or the set temperature of the heater 27 may be adjusted based on the detected temperature. Good.
  • the oil tank 23 is partitioned by a partition plate 43 and divided into a separation region 41 and a discharge region 42.
  • the partition plate 43 is a plate-like member, and the side end portion contacts the inner side surface of the oil tank 23. As a result, the oil tank 23 is divided into two regions with the partition plate 43 as a boundary.
  • On the lubricating oil discharge line 25 side of the partition plate 43 is a separation region 41 into which the lubricating oil returned from the housing 30 flows. Further, the lubricating oil supply line 22 side of the partition plate 43 is a discharge region 42 where the lubricating oil is supplied to the housing 30.
  • the separation region 41 is supplied with the lubricating oil in which the refrigerant is dissolved from the lubricating oil discharge line 25.
  • the lubricating oil in which the refrigerant has dissolved has a higher specific gravity than the refrigerant alone or the lubricating oil alone, and has a high concentration at the bottom surface of the separation region 41.
  • coolant is heated and gasified by the heater 27 arrange
  • the space in which the lubricating oil is stored is limited by the partition plate 43, so that the lubricating oil can be efficiently heated by the heater 27.
  • a plurality of flow forming plates 44 other than the partition plate 43 described above may be provided.
  • the flow forming plate 44 By installing the flow forming plate 44 in the separation region 41, the flow of the lubricating oil from the upper part to the lower part or the flow from the lower part to the upper part can be formed in the stored lubricating oil. Thereby, the lubricating oil can be efficiently brought into contact with the heater 27, or the separated and gasified refrigerant can be raised upward.
  • the heated and gasified refrigerant rises above the lubricating oil stored in the oil tank 23. Even when the forming phenomenon occurs, the foamed lubricating oil rises along the partition plate 43 and the flow forming plate 44, and then the foam floats on the liquid lubricating oil. Therefore, in the present embodiment, unlike the case where there is no partition plate 43 or flow forming plate 44, bubbles due to the refrigerant gas hardly flow to the downstream side inside the liquid lubricating oil. As a result, it is possible to prevent bubbles from being sucked into the oil tank 23.
  • the lubricating oil stored in the oil tank 23 is caused to flow in one direction by the oil pump 36, that is, from the lubricating oil / refrigerant inlet side to the lubricating oil outlet side.
  • the oil pump 36 that is, from the lubricating oil / refrigerant inlet side to the lubricating oil outlet side.
  • the lubricating oil whose refrigerant concentration is reduced due to the separation of the refrigerant flows toward the lubricating oil outlet side.
  • bubbles floating on the lubricating oil also flow toward the downstream side along the flow of the lubricating oil.
  • the lower end part of the partition plate 43 or the flow forming plate 44 may be in contact with the bottom surface of the oil tank 23 or may be separated from the bottom surface.
  • a flow from the lower part to the upper part is formed in the lubricating oil.
  • the lubricating oil in which the refrigerant has melted flows downstream without staying at the bottom in the separation region 41. At this time, the lubricating oil in which the refrigerant is dissolved flows along the heater 27, whereby the refrigerant can be efficiently gasified.
  • one partition plate 43 and two flow forming plates 44 are installed is illustrated, but the present invention is not limited to this example.
  • one partition plate 43 and one flow forming plate 44 may be installed.
  • an oil pump 36 is installed in the discharge area 42.
  • the oil pump 36 is an immersion pump, for example, and is installed on the bottom surface of the oil tank 23.
  • the oil pump 36 sucks the lubricating oil at the bottom of the oil tank 23 and supplies the lubricating oil to the outside, that is, the housing 30.
  • the bubbles rise in the separation region 41, so that the oil pump 36 installed in the discharge region 42 is difficult to suck the refrigerant gas.
  • the heater 27 may be installed only in the upstream separation region 41, or may be installed in the downstream discharge region 42 as shown in FIG. In addition, by installing the heater 27 in the discharge region 42, the amount of refrigerant separated from the lubricating oil can be increased. However, if there is a possibility that a forming phenomenon may occur due to heating by the heater 27 in the discharge area 42, it is better not to install the heater 27 in the discharge area 42.
  • the buffer tank 28 is installed in the pressure equalizing pipe 29.
  • the buffer tank 28 can store foamy lubricating oil flowing out from the oil tank 23 and has a capacity that prevents the lubricating oil from flowing out to the pressure equalizing pipe 29 on the downstream side.
  • An inlet portion connected to a pressure equalizing pipe 29 connected to the oil tank 23 is formed in the upper portion of the buffer tank 28. Further, an outlet portion is formed at a portion different from the inlet portion at the upper portion of the buffer tank 28, and the outlet portion is connected to a pressure equalizing pipe 29 connected to the evaporator 8.
  • the refrigerant and lubricating oil that have flowed out of the oil tank 23 are supplied to the buffer tank 28 via the pressure equalizing pipe 29. Then, the lubricating oil flowing out from the oil tank 23 is temporarily stored in the buffer tank 28. In addition, the gasified refrigerant dissolved in the lubricating oil flows from the buffer tank 28 to the evaporator 8.
  • the lubricating oil is stored in the buffer tank 28 and does not flow to the refrigeration cycle, but only the refrigerant. Heads for the refrigeration cycle.
  • a return pipe 26 is connected below the oil tank 23.
  • One end of the return pipe 26 is connected to the bottom surface of the buffer tank 28, for example, and the other end is connected to the oil tank 23.
  • the return pipe 26 is provided separately from the pressure equalizing pipe 29 and returns the lubricating oil stored in the buffer tank 28 to the oil tank 23. As a result, the lubricating oil that has flowed out of the oil tank 23 and accumulated in the buffer tank 28 is returned to the oil tank 23 without flowing into the refrigerant cycle.
  • the position where the return pipe 26 is connected to the oil tank 23 is the side close to the position where the lubricating oil supply line 22 is connected in the oil tank 23. Thereby, the lubricating oil returned from the buffer tank 28 is returned to the vicinity of the position where the lubricating oil supply line 22 is connected in the oil tank 23, for example, to the discharge region 42. Even when forming occurs in the oil tank 23, it is mixed with lubricating oil not affected by the forming.
  • Lubricating oil is stored in the oil tank 23 and is supplied from the oil tank 23 to the turbo compressor 2 by the oil pump 36.
  • the lubricating oil supplied to the turbo compressor 2 is supplied to the gears 17 and 18 and the rolling bearing 14 inside the motor housing 31 and the speed increaser housing 32 of the turbo compressor 2.
  • Lubricating oil supplied to the gears 17 and 18 and the rolling bearing 14 rises in temperature due to friction loss while lubricating the gears 17 and 18 and the rolling bearing 14.
  • the lubricating oil that has passed through the motor housing 31 and the speed increaser housing 32 of the turbo compressor 2 passes through the oil cooler 24 and is cooled.
  • the lubricating oil that has passed through the gears 17 and 18 and the rolling bearing 14 in the motor housing 31 and the speed increaser housing 32 of the turbo compressor 2 is cooled by the oil cooler 24.
  • the lubricating oil and refrigerant discharged to the oil tank 23 flow downward in the separation region 41 and are heated by the heater 27 installed in the lower part of the oil tank 23, and the refrigerant evaporates. As a result, the kinematic viscosity of the lubricating oil diluted with the refrigerant is restored.
  • Lubricating oil in which the refrigerant has evaporated and the refrigerant content has decreased flows to the downstream side of the oil tank 23. Further, the refrigerant gas evaporated by the heater 27 is directed upward of the oil tank 23, and is supplied from the oil tank 23 through the pressure equalizing pipe 29 to the evaporator 8 through the pressure equalizing pipe 29 and the buffer tank 28.
  • the refrigerant and the lubricating oil flowing out from the oil tank 23 are supplied to the buffer tank 28 via the pressure equalizing pipe 29, and the lubricating oil is temporarily stored in the buffer tank 28.
  • the lubricating oil is stored in the buffer tank 28 and does not flow to the refrigeration cycle, but only the refrigerant enters the refrigeration cycle. Head.
  • the lubricating oil in which the refrigerant is dissolved is supplied to the separation region 41 of the oil tank 23, and the lubricating oil in which the refrigerant is dissolved in the separation region 41 is separated into the lubricating oil and the refrigerant.
  • the separated lubricating oil is supplied from the separation region 41 to the discharge region 42 and supplied into the housing 30. Since the separation region 41 and the discharge region 42 are partitioned by the partition plate 43, the lubricating oil that has flowed into the oil tank 23 in the separation region 41 is different in the specific gravity of the lubricating oil and the refrigerant and the lubricating oil in a narrow space. It is efficiently separated by utilizing the temperature rise of Further, by installing the partition plate 43, it is possible to prevent the foamed lubricating oil from flowing toward the discharge region 42 even if the forming phenomenon occurs in the separation region 41.
  • the amount of lubricating oil flowing out to the refrigeration cycle such as the evaporator 8 can be reduced. Further, the amount of refrigerant sucked by the oil pump 36 can be reduced, and the amount of lubricating oil circulating in the lubricating oil system can be prevented from being reduced.

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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)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Lubricants (AREA)

Abstract

Le but de la présente invention est de fournir un réfrigérateur dans lequel la capacité du réservoir d'huile peut être rendue plus petite que d'habitude pendant qu'un phénomène de moussage est adressé. Le réfrigérateur est pourvu : d'un cycle de réfrigération qui comprend un condenseur, un évaporateur, et un compresseur électrique ayant un mécanisme de compression destiné à être entraîné par un moteur et dans lequel circule un réfrigérant; un réservoir d'huile (23) dans lequel est stockée une huile lubrifiante; un dispositif de chauffage (27) qui est placé dans le réservoir d'huile (23) et qui chauffe l'huile lubrifiante; une conduite d'alimentation en huile lubrifiante (22) qui est raccordée au réservoir d'huile (23) et qui fournit l'huile lubrifiante à partir du réservoir d'huile (23) dans le carter logeant le moteur; une conduite d'évacuation d'huile lubrifiante (25) qui renvoie l'huile lubrifiante du carter au réservoir d'huile (23); un tuyau d'égalisation de pression (29) dont une extrémité est reliée au réservoir d'huile (23) et dont l'autre extrémité est reliée au cycle de réfrigération; et un réservoir tampon (28) qui est fixé au tuyau d'égalisation de pression (29), qui reçoit le réfrigérant et l'huile lubrifiante s'écoulant à partir du réservoir d'huile (23), et dans lequel l'huile lubrifiante est stockée.
PCT/JP2017/023420 2016-06-30 2017-06-26 Réfrigérateur WO2018003748A1 (fr)

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CN201780016599.XA CN108779946B (zh) 2016-06-30 2017-06-26 制冷机
US16/081,612 US20190078811A1 (en) 2016-06-30 2017-06-26 Refrigerator

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JP2016-130103 2016-06-30
JP2016130103A JP2018004142A (ja) 2016-06-30 2016-06-30 冷凍機

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WO2018003748A1 true WO2018003748A1 (fr) 2018-01-04

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JP6736357B2 (ja) * 2016-05-31 2020-08-05 三菱重工サーマルシステムズ株式会社 ターボ冷凍機及びその起動制御方法
CN111854231A (zh) * 2019-04-26 2020-10-30 荏原冷热系统（中国）有限公司 离心式制冷机所使用的油箱以及离心式制冷机
US11898571B2 (en) 2021-12-30 2024-02-13 Trane International Inc. Compressor lubrication supply system and compressor thereof

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JPS5282958U (fr) * 1975-12-16 1977-06-21
JPS5318042A (en) * 1976-08-02 1978-02-18 Hitachi Plant Eng & Constr Co Ltd Oil collecting system in refrigeration cycle
JPS59132060U (ja) * 1983-02-23 1984-09-04 株式会社日立製作所 タ−ボ冷凍機用油分離装置
JPH02178579A (ja) * 1988-12-29 1990-07-11 Daikin Ind Ltd ターボ冷凍機の潤滑装置
JPH0363476A (ja) * 1989-08-02 1991-03-19 Hitachi Ltd 冷凍機
WO2002006740A1 (fr) * 2000-07-13 2002-01-24 Mitsubishi Heavy Industries, Ltd. Éjecteur et machine à réfrigérer
JP2008082622A (ja) * 2006-09-27 2008-04-10 Ebara Corp 圧縮式冷凍装置
JP2012163262A (ja) * 2011-02-07 2012-08-30 Mitsubishi Heavy Ind Ltd 棒状ヒータ及びターボ冷凍機
JP2014145345A (ja) * 2013-01-30 2014-08-14 Mitsubishi Heavy Ind Ltd ターボ圧縮機及びターボ冷凍機

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JPS5282958A (en) * 1975-12-30 1977-07-11 Toyoda Gosei Kk Heating disque of molding machine
US5724821A (en) * 1996-06-28 1998-03-10 Carrier Corporation Compressor oil pressure control method
CN104896989A (zh) * 2014-03-05 2015-09-09 珠海格力电器股份有限公司 油冷却系统及油冷却器

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5282958U (fr) * 1975-12-16 1977-06-21
JPS5318042A (en) * 1976-08-02 1978-02-18 Hitachi Plant Eng & Constr Co Ltd Oil collecting system in refrigeration cycle
JPS59132060U (ja) * 1983-02-23 1984-09-04 株式会社日立製作所 タ−ボ冷凍機用油分離装置
JPH02178579A (ja) * 1988-12-29 1990-07-11 Daikin Ind Ltd ターボ冷凍機の潤滑装置
JPH0363476A (ja) * 1989-08-02 1991-03-19 Hitachi Ltd 冷凍機
WO2002006740A1 (fr) * 2000-07-13 2002-01-24 Mitsubishi Heavy Industries, Ltd. Éjecteur et machine à réfrigérer
JP2008082622A (ja) * 2006-09-27 2008-04-10 Ebara Corp 圧縮式冷凍装置
JP2012163262A (ja) * 2011-02-07 2012-08-30 Mitsubishi Heavy Ind Ltd 棒状ヒータ及びターボ冷凍機
JP2014145345A (ja) * 2013-01-30 2014-08-14 Mitsubishi Heavy Ind Ltd ターボ圧縮機及びターボ冷凍機

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CN108779946B (zh) 2020-09-18
JP2018004142A (ja) 2018-01-11
US20190078811A1 (en) 2019-03-14

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