WO2023218865A1 - Compresseur du type à lubrification par huile pour cryoréfrigérateur - Google Patents

Compresseur du type à lubrification par huile pour cryoréfrigérateur Download PDF

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Publication number
WO2023218865A1
WO2023218865A1 PCT/JP2023/015355 JP2023015355W WO2023218865A1 WO 2023218865 A1 WO2023218865 A1 WO 2023218865A1 JP 2023015355 W JP2023015355 W JP 2023015355W WO 2023218865 A1 WO2023218865 A1 WO 2023218865A1
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Prior art keywords
oil
heat exchanger
cooled heat
compressor
air
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PCT/JP2023/015355
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English (en)
Japanese (ja)
Inventor
翔 鈴木
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住友重機械工業株式会社
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Publication of WO2023218865A1 publication Critical patent/WO2023218865A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point

Definitions

  • the present invention relates to an oil-lubricated compressor for a cryogenic refrigerator.
  • An oil-lubricated helium compressor with dual aftercoolers has been proposed (see, for example, Patent Document 1).
  • This compressor has two built-in aftercoolers for cooling helium and oil: a water-cooled aftercooler and an air-cooled aftercooler.
  • the air-cooled aftercooler is arranged in series or parallel with the water-cooled aftercooler. Activating the air-cooled aftercooler's fan provides redundancy in the event that the water-cooled aftercooler's cooling water circuit is blocked.
  • the present inventor studied the above-mentioned helium compressor and recognized the following problems. Since this compressor is equipped with two heat exchangers, one water-cooled and one air-cooled, the total length of the oil line to be cooled tends to be long, which can increase pressure loss in the oil flow. . The resulting decrease in oil flow rate can reduce cooling capacity, which can lead to compressor overheating and shortened service life due to high-temperature operation. In particular, if the temperature of the cooling water supplied to the water-cooled heat exchanger is too low, this problem is likely to occur because the oil viscosity may increase nonlinearly at such a low temperature. A possible measure is to restore the oil flow rate by increasing input energy, for example by driving the oil pump with high power. However, this undesirably increases power consumption.
  • One exemplary objective of an embodiment of the present invention is to reduce pressure loss in an oil line in an oil-lubricated compressor for a cryogenic refrigerator.
  • an oil-lubricated compressor for a cryogenic refrigerator includes an air-cooled heat exchanger including a cooling fan, a first oil line arranged to be forcibly cooled by the cooling fan, and a second oil line that bypasses the first oil line. , is provided.
  • pressure loss in an oil line in an oil-lubricated compressor for a cryogenic refrigerator can be reduced.
  • FIG. 1 is a diagram schematically showing a cryogenic refrigerator according to an embodiment.
  • FIG. 2 is a diagram schematically showing an example of an oil circulation line of a compressor according to an embodiment. It is a figure which shows roughly another example of the oil circulation line of the compressor based on embodiment.
  • FIG. 1 is a diagram schematically showing a cryogenic refrigerator according to an embodiment.
  • the cryogenic refrigerator 10 includes an oil-lubricated cryogenic refrigerator compressor (hereinafter also simply referred to as a compressor) 12 and a cold head 14.
  • the compressor 12 is configured to collect refrigerant gas from the cryogenic refrigerator 10 from the cold head 14, pressurize the collected refrigerant gas, and supply the refrigerant gas to the cold head 14 again.
  • Compressor 12 is also referred to as a compressor unit.
  • the cold head 14 is also called an expander, and has a room temperature section 14a and a low temperature section 14b, also called a cooling stage.
  • the compressor 12 and the cold head 14 constitute a refrigeration cycle of the cryogenic refrigerator 10, whereby the low temperature section 14b is cooled to a desired cryogenic temperature.
  • the refrigerant gas also referred to as the working gas, is typically helium gas, although other suitable gases may be used.
  • the cryogenic refrigerator 10 is, by way of example, a single-stage or two-stage Gifford-McMahon (GM) refrigerator, but may also be a pulse tube refrigerator, a Stirling refrigerator, or other types of cryogenic refrigerators. It may also be a refrigerator. Although the cold head 14 has different configurations depending on the type of cryogenic refrigerator 10, the compressor 12 can have the configuration described below regardless of the type of cryogenic refrigerator 10.
  • GM Gifford-McMahon
  • the pressure of the refrigerant gas supplied from the compressor 12 to the cold head 14 and the pressure of the refrigerant gas recovered from the cold head 14 to the compressor 12 are both significantly higher than atmospheric pressure, and are respectively at the first high pressure and It can be called the second high pressure.
  • the first high pressure and the second high pressure are also simply referred to as high pressure and low pressure, respectively.
  • the high pressure is for example 2-3 MPa.
  • the low pressure is, for example, 0.5 to 1.5 MPa, for example about 0.8 MPa.
  • the compressor 12 includes a compressor main body 16, a refrigerant gas line 18, an oil circulation line 20, and a compressor cooling system 22.
  • the refrigerant gas line 18 is shown as a solid line
  • the oil circulation line 20 is shown as a broken line.
  • the compressor cooling system 22 includes a liquid-cooled heat exchanger 24 and an air-cooled heat exchanger 26, and is configured to cool the refrigerant gas line 18 and the oil circulation line 20.
  • the compressor 12 also includes a compressor housing 28 that accommodates each component of the compressor 12, such as the compressor main body 16, refrigerant gas line 18, oil circulation line 20, and compressor cooling system 22.
  • the compressor main body 16 is configured to internally compress refrigerant gas sucked in from its suction port and discharge it from its discharge port. Oil is used in the compressor body 16 for cooling and lubrication, and the sucked refrigerant gas is directly exposed to this oil within the compressor body 16. Therefore, the refrigerant gas is sent out from the discharge port with some oil mixed therein.
  • the compressor main body 16 may be, for example, a scroll type, rotary type, or other pump that increases the pressure of refrigerant gas.
  • Compressor body 16 may be configured to deliver a fixed, constant flow rate of refrigerant gas.
  • the compressor main body 16 may be configured to vary the flow rate of refrigerant gas to be discharged.
  • the compressor body 16 is sometimes referred to as a compression capsule.
  • the refrigerant gas line 18 includes a discharge port 30, a suction port 31, a discharge passage 32, and a suction passage 33.
  • the discharge port 30 is a refrigerant gas outlet installed in the compressor casing 28 to send out the refrigerant gas pressurized to high pressure by the compressor main body 16 from the compressor 12, and the suction port 31 is a refrigerant gas outlet installed in the compressor housing 28 to send out the refrigerant gas pressurized to high pressure by the compressor main body 16.
  • a refrigerant gas inlet located in the compressor housing 28 for receiving gas into the compressor 12.
  • the discharge flow path 32 and the suction flow path 33 are housed in the compressor housing 28.
  • a discharge port of the compressor body 16 is connected to a discharge port 30 through a discharge passage 32, and a suction port 31 is connected to an inlet of the compressor body 16 through a suction passage 33.
  • the discharge flow path 32 is provided with a liquid-cooled heat exchanger 24 and an air-cooled heat exchanger 26 that constitute the compressor cooling system 22.
  • an oil separator 34 and an adsorber 35 are provided in the discharge flow path 32 downstream of the compressor cooling system 22.
  • the oil separator 34 is provided to separate oil that is mixed into the refrigerant gas by passing through the compressor main body 16 from the refrigerant gas.
  • the adsorber 35 is provided to remove, for example, vaporized oil and other contaminant components remaining in the refrigerant gas from the refrigerant gas by adsorption.
  • the oil separator 34 and the adsorber 35 are connected in series.
  • the oil separator 34 is arranged on the compressor main body 16 side, and the adsorber 35 is arranged on the discharge port 30 side.
  • An oil return line 21 is provided that connects the oil separator 34 to the compressor body 16.
  • the oil collected by the oil separator 34 can be returned to the compressor body 16 through the oil return line 21 .
  • a filter for removing dust contained in the oil separated by the oil separator 34 and an orifice for controlling the amount of oil returned to the compressor body 16 may be provided in the middle of the oil return line 21 .
  • a storage tank 36 is provided in the suction flow path 33.
  • the storage tank 36 is provided as a volume for removing pulsations contained in the low pressure refrigerant gas returning from the cold head 14 to the compressor 12.
  • the refrigerant gas line 18 is provided with a bypass valve 38 that connects the discharge passage 32 to the suction passage 33 so as to bypass the compressor main body 16.
  • the bypass valve 38 branches from the discharge passage 32 between the oil separator 34 and the adsorber 35, and is connected to the suction passage 33 between the compressor main body 16 and the storage tank 36.
  • the bypass valve 38 is provided for controlling the flow rate of refrigerant gas and/or for equalizing the pressures between the discharge passage 32 and the suction passage 33 when the compressor 12 is stopped.
  • the refrigerant gas line 18 of the compressor 12 is connected to the cold head 14.
  • a high pressure port 40 and a low pressure port 41 are provided in the room temperature section 14a of the cold head 14.
  • the high pressure port 40 is connected to the discharge port 30 by a high pressure pipe 42, and the low pressure port 41 is connected to the suction port 31 by a low pressure pipe 43.
  • the oil circulation line 20 connects the oil outlet of the compressor body 16 to the oil inlet via the compressor cooling system 22 (that is, the liquid-cooled heat exchanger 24 and the air-cooled heat exchanger 26). Therefore, the oil flowing out from the compressor main body 16 can be cooled by the compressor cooling system 22 and can flow into the compressor main body 16 again.
  • the oil circulation line 20 branches into a plurality of (two in this example) oil flow paths in the compressor cooling system 22, as described below. These branched oil flow paths rejoin between the compressor cooling system 22 and the oil inlet of the compressor body 16.
  • the oil circulation line 20 may be provided with an orifice that controls the flow rate of oil flowing inside. Further, the oil circulation line 20 may be provided with a filter that removes dust contained in the oil. Such orifices and filters may be provided, for example, downstream of the oil circulation line 20, ie between the compressor cooling system 22 and the oil inlet of the compressor body 16.
  • the compressor cooling system 22 includes the liquid-cooled heat exchanger 24 and the air-cooled heat exchanger 26.
  • the liquid-cooled heat exchanger 24 and the air-cooled heat exchanger 26 are connected in series, and the liquid-cooled heat exchanger 24 is provided upstream of the air-cooled heat exchanger 26. Therefore, the oil and high-pressure refrigerant gas heated by the heat of compression generated as the refrigerant gas is compressed in the compressor main body 16 first flows into the liquid-cooled heat exchanger 24 from the compressor main body 16 and is cooled, and then cools. It flows into the air-cooled heat exchanger 26.
  • the liquid-cooled heat exchanger 24 is mounted on the compressor 12 as a main cooling device for the compressor 12, and the air-cooled heat exchanger 26 is mounted on the compressor 12 as a preliminary cooling device for the compressor 12. There is. Therefore, the liquid-cooled heat exchanger 24 always operates while the compressor 12 is operating, and the air-cooled heat exchanger 26 does not operate when the liquid-cooled heat exchanger 24 is operating normally, and if the liquid-cooled heat exchanger 24 is malfunctioning. It may be activated when it is not activated due to reasons such as, or when its cooling capacity is reduced. Therefore, as will be described later, the air-cooled heat exchanger 26 may be configured to turn itself on and off based on the output of a sensor provided in the compressor 12, such as an oil or refrigerant gas temperature sensor.
  • the liquid-cooled heat exchanger 24 includes a first part 24a that cools the refrigerant gas by heat exchange between the refrigerant gas and the coolant, and a second part 24b that cools the oil by heat exchange between the oil and the coolant.
  • the first portion 24a is disposed in the discharge passage 32 between the compressor body 16 and the oil separator 34, more specifically between the discharge port of the compressor body 16 and the air-cooled heat exchanger 26, and is arranged in the discharge passage 32.
  • the refrigerant gas flowing through 32 is cooled.
  • the second portion 24b is disposed in the oil circulation line 20 between the oil outlet of the compressor body 16 and the air-cooled heat exchanger 26, and cools the oil flowing through the oil circulation line 20.
  • Cooling liquid eg, tap water, industrial water, etc.
  • the cooling liquid is supplied to the compressor 12 from the outside, passes through the first portion 24a and the second portion 24b of the liquid-cooled heat exchanger 24, and is discharged to the outside of the compressor 12. In this way, the heat of compression generated in the compressor body 16 is removed out of the compressor 12 along with the cooling fluid.
  • the coolant may be cooled by a coolant circulation device (not shown) such as a known water chiller, and then supplied to the compressor 12 again.
  • the air-cooled heat exchanger 26 includes a cooling fan 50 , a first oil line 46 arranged to be forcibly cooled by the cooling fan 50 , and a first oil line 46 that bypasses the first oil line 46 and is forcibly cooled by the cooling fan 50 .
  • a second oil line 48 is provided.
  • the first oil line 46 and the second oil line 48 are part of the oil circulation line 20 disposed within the air-cooled heat exchanger 26.
  • the second oil line 48 branches from the oil circulation line 20 upstream of the air-cooled heat exchanger 26, that is, between the liquid-cooled heat exchanger 24 and the air-cooled heat exchanger 26, and branches downstream of the air-cooled heat exchanger 26, that is, between the liquid-cooled heat exchanger 24 and the air-cooled heat exchanger 26. It joins the first oil line 46 again between the cold heat exchanger 26 and the oil inlet of the compressor main body 16 .
  • the cooling fan 50 is installed in the compressor housing 28 so as to discharge air from the air-cooled heat exchanger 26 to the outside when the cooling fan 50 is operated.
  • Two air intake ports 52 are provided in a portion of the compressor housing 28 that surrounds the air-cooled heat exchanger 26.
  • air is supplied from the outside to the air-cooled heat exchanger 26 through these air intake ports 52. air is taken in.
  • the air flow blown into the air-cooled heat exchanger 26 from one air intake port 52 is used for forced air cooling of the refrigerant gas line 18 and the first oil line 46, and the air flow is blown into the air-cooled heat exchanger 26 from the other air intake port 52.
  • Another blowing air flow is used for forced air cooling of the second oil line 48.
  • these air flows are schematically shown by thick arrows for understanding.
  • the cooling fan 50 may operate based on the oil temperature measured by an oil temperature sensor.
  • the cooling fan 50 may operate based on the refrigerant gas temperature measured by a refrigerant gas temperature sensor.
  • refrigerant gas recovered from the cold head 14 to the compressor 12 flows from the low pressure port 41 to the suction port 31 of the compressor 12 through the low pressure pipe 43.
  • the refrigerant gas passes through the storage tank 36 on the suction flow path 33 and is recovered to the suction port of the compressor body 16.
  • the refrigerant gas is compressed and pressurized by the compressor main body 16.
  • the refrigerant gas sent out from the discharge port of the compressor main body 16 is cooled by the liquid-cooled heat exchanger 24 and the air-cooled heat exchanger 26, and further passes through the oil separator 34 and the adsorber 35 before exiting the compressor 12 from the discharge port 30.
  • Refrigerant gas is supplied into the cold head 14 via the high pressure pipe 42 and the high pressure port 40.
  • the oil flowing out from the oil outlet of the compressor body 16 flows into the liquid-cooled heat exchanger 24 through the oil circulation line 20, and is cooled by heat exchange between the oil and the cooling liquid in the liquid-cooled heat exchanger 24.
  • the cooled oil flows from the liquid-cooled heat exchanger 24 to the air-cooled heat exchanger 26 .
  • the oil branches into a first oil line 46 and a second oil line 48 and flows within the air-cooled heat exchanger 26 .
  • the cooling fan 50 When the cooling fan 50 is operating, the oil is cooled by air as it flows through the first oil line 46 and the second oil line 48 . Oil exiting the air-cooled heat exchanger 26 is returned to the oil inlet of the compressor body 16 through the oil circulation line 20.
  • the compressor 12 may be provided with various sensors.
  • compressor 12 may include at least one oil temperature sensor (61-63) that measures the temperature of the oil.
  • the first sensor 61 is provided upstream of the liquid-cooled heat exchanger 24 on the oil circulation line 20 and measures the temperature of the oil flowing into the liquid-cooled heat exchanger 24 from the compressor main body 16 .
  • the second sensor 62 is provided downstream of the liquid-cooled heat exchanger 24 on the oil circulation line 20, specifically between the liquid-cooled heat exchanger 24 and the air-cooled heat exchanger 26, and is configured to provide air-cooled heat exchange from the liquid-cooled heat exchanger 24 to the air-cooled heat exchanger 26.
  • the temperature of the oil flowing into the vessel 26 is measured.
  • the third sensor 63 is provided downstream of the air-cooled heat exchanger 26 on the oil circulation line 20 and measures the temperature of the oil flowing into the compressor body 16 from the air-cooled heat exchanger 26 .
  • the temperature sensor may be a thermistor, for example.
  • the compressor 12 may include at least one refrigerant gas sensor (64 to 66) that measures the temperature of refrigerant gas.
  • the fourth sensor 64 is provided upstream of the liquid-cooled heat exchanger 24 on the discharge flow path 32 of the refrigerant gas line 18 and measures the temperature of the refrigerant gas flowing into the liquid-cooled heat exchanger 24 from the compressor main body 16 .
  • the fifth sensor 65 is provided downstream of the liquid-cooled heat exchanger 24 on the refrigerant gas line 18, specifically between the liquid-cooled heat exchanger 24 and the air-cooled heat exchanger 26, and is arranged to exchange heat from the liquid-cooled heat exchanger 24 to the air-cooled heat exchanger 26. The temperature of the refrigerant gas flowing into the vessel 26 is measured.
  • the sixth sensor 66 is provided downstream of the air-cooled heat exchanger 26 on the refrigerant gas line 18 and measures the temperature of the refrigerant gas flowing into the oil separator 34 from the air-cooled heat exchanger 26 .
  • the air-cooled heat exchanger 26 may be provided with a fan controller 54 that turns the cooling fan 50 on and off.
  • the fan controller 54 is configured to receive a sensor signal from at least one sensor indicating a measurement result of the sensor, and operate the cooling fan 50 based on the measurement result. Note that FIG. 1 shows, as an example, a case where a sensor signal from the second sensor 62 is input to the fan controller 54.
  • the fan controller 54 is realized as a hardware configuration by elements and circuits such as a computer's CPU and memory, and as a software configuration is realized by a computer program, etc., but in the figure, it is realized by the cooperation of these as appropriate. It is depicted as a functional block. Those skilled in the art will understand that these functional blocks can be implemented in various ways by combining hardware and software.
  • the fan controller 54 may operate the cooling fan 50 based on the oil temperature measured by at least one oil temperature sensor (61-63).
  • the fan controller 54 receives a sensor signal indicating the measured temperature of the oil from the first sensor 61, the second sensor 62, or the third sensor 63, and compares this measured temperature with a temperature threshold.
  • This temperature threshold is set to a value at which oil cooling is evaluated to be insufficient if the oil temperature is higher than this threshold.
  • the oil temperature measured by the oil temperature sensor exceeds the temperature threshold is, for example, if the temperature of the coolant supplied to the liquid-cooled heat exchanger 24 is too high (i.e., the temperature of the chiller that cools the coolant is too high). (defect or breakdown) or a defect in the liquid-cooled heat exchanger 24 itself (clogged or damaged heat exchanger).
  • the fan controller 54 operates the air-cooled heat exchanger 26 when the measured temperature exceeds the temperature threshold. That is, the fan controller 54 starts the air-cooled heat exchanger 26 by switching the cooling fan 50 from off to on. On the other hand, if the measured temperature does not exceed the temperature threshold, the fan controller 54 does not activate the air-cooled heat exchanger 26 (keeps the cooling fan 50 off). In this manner, by operating the air-cooled heat exchanger 26, which is a preliminary cooling device for the compressor 12, it is possible to cope with a malfunction of the liquid-cooled heat exchanger 24, which is the main cooling device for the compressor 12.
  • the fan controller 54 may operate the cooling fan 50 based on the refrigerant gas temperature measured by the refrigerant gas temperature sensor. For example, the fan controller 54 may receive a sensor signal indicating the measured temperature of the refrigerant gas from the fourth sensor 64 or the fifth sensor 65, and may compare the measured temperature with a temperature threshold. Fan controller 54 activates air-cooled heat exchanger 26 when the measured temperature exceeds the temperature threshold, and does not activate air-cooled heat exchanger 26 when the measured temperature does not exceed the temperature threshold. Even in this case, malfunction of the liquid-cooled heat exchanger 24 can be dealt with using the air-cooled heat exchanger 26.
  • cryogenic refrigerator 10 cooling superconducting magnets.
  • a superconducting magnet is cooled by immersing it in a large amount of liquid helium, and the cryogenic refrigerator 10 is used to cool and recondense the liquid helium.
  • the cryocooler 10 is shut down, large amounts of liquid helium can keep the superconducting magnet cool for some time.
  • research and development has been progressing on superconducting magnets that can significantly reduce the amount of liquid helium used.
  • stopping operation of the cryogenic refrigerator 10 tends to directly lead to loss of cooling of the superconducting magnet.
  • the compressor cooling system 22 since the compressor cooling system 22 includes the liquid-cooled heat exchanger 24 and the air-cooled heat exchanger 26, redundancy in cooling the compressor 12 is ensured. Even if the liquid-cooled heat exchanger 24 malfunctions, the cooling function of the compressor 12 can be supplemented or replaced by the air-cooled heat exchanger 26. Therefore, the risk of excessive temperature rise of the compressor 12 and the resulting shutdown of the cryogenic refrigerator 10 is reduced. Therefore, the cryogenic refrigerator 10 according to the embodiment is useful for improving the operational continuity of a so-called helium-saving type superconducting device.
  • the compressor cooling system 22 is equipped with two heat exchangers, a liquid-cooled type and an air-cooled type (in particular, the liquid-cooled heat exchanger 24 and the air-cooled heat exchanger 26 are connected in series). Therefore, the total length of the oil circulation line 20 to be cooled tends to be long, which may increase the pressure loss of the oil flow. The resulting decrease in the oil flow rate in the oil circulation line 20 may reduce the cooling capacity of the compressor cooling system 22, which may lead to overheating of the compressor 12 and shortening of its life due to high temperature operation. In particular, if the temperature of the coolant supplied to the liquid-cooled heat exchanger 24 is too low, this problem is likely to occur because the oil viscosity may increase nonlinearly at such a low temperature. A possible measure is to restore the oil flow rate in the oil circulation line 20 by increasing the input energy, for example by driving the oil pump with high power. However, this undesirably increases power consumption.
  • the air-cooled heat exchanger 26 does not have only the first oil line 46, but further includes a second oil line 48 that bypasses the first oil line 46.
  • the passage cross-sectional area of the oil circulation line 20 increases and pressure loss can be reduced. Even if the oil is cooled to a low temperature in the liquid-cooled heat exchanger 24 and the viscosity of the oil discharged from the liquid-cooled heat exchanger 24 increases, a decrease in the oil flow rate flowing through the air-cooled heat exchanger 26 can be suppressed. Insufficient flow of oil circulating through the oil circulation line 20 can be prevented, and insufficient cooling of the compressor 12 can be avoided.
  • FIG. 2 is a diagram schematically showing an example of the oil circulation line 20 of the compressor 12 according to the embodiment.
  • the compressor 12 includes a compressor main body 16, a compressor cooling system 22, and an oil circulation line 20 connecting these.
  • the compressor cooling system 22 includes a liquid-cooled heat exchanger 24 and an air-cooled heat exchanger 26, and is configured to cool the oil circulation line 20.
  • the liquid-cooled heat exchanger 24 and the air-cooled heat exchanger 26 are connected in series, and the liquid-cooled heat exchanger 24 is provided upstream of the air-cooled heat exchanger 26.
  • the oil circulation line 20 branches into a first oil line 46 and a second oil line 48 upstream of the air-cooled heat exchanger 26, that is, between the liquid-cooled heat exchanger 24 and the air-cooled heat exchanger 26.
  • the air-cooled heat exchanger 26 includes a cooling fan 50, and the first oil line 46 and the second oil line 48 are forcibly cooled by the air flow generated within the air-cooled heat exchanger 26 when the cooling fan 50 operates.
  • the first oil line 46 and the second oil line 48 join together again downstream of the air-cooled heat exchanger 26, that is, between the air-cooled heat exchanger 26 and the oil inlet of the compressor body 16.
  • the air-cooled heat exchanger 26 is provided in at least one of the first oil line 46 and the second oil line 48 so as to reduce the difference between the oil flow rate in the first oil line 46 and the oil flow rate in the second oil line 48.
  • An orifice 56 may also be provided.
  • the oil flow rate in the second oil line 48 is larger than that in the first oil line 46 when the orifice 56 is not present. Therefore, by providing the orifice 56 in the second oil line 48, the oil flow rate in the second oil line 48 can be reduced and the oil flow rates in the first oil line 46 and the second oil line 48 can be equalized. It is possible to eliminate the imbalance in oil flow rates between the first oil line 46 and the second oil line 48, and improve the heat exchange efficiency of the air-cooled heat exchanger 26.
  • the hole diameter R [m] of the orifice 56 may be selected from the range of 1.0 ⁇ 10 ⁇ 4 (m) ⁇ R ⁇ 5.0 ⁇ 10 ⁇ 2 (m).
  • the pore diameter R can be calculated using the following formula.
  • ⁇ is the viscosity [Pa ⁇ s] of the oil flowing into the air-cooled heat exchanger
  • L 1 and L 2 are the lengths of the first oil line 46 and the second oil line 48 as the air-cooled heat exchanger, respectively.
  • [m] and d represent the pipe diameters [m] of the first oil line 46 and the second oil line 48
  • Q represents the oil flow rate [m 3 /s] of the oil circulation line 20.
  • FIG. 3 is a diagram schematically showing another example of the oil circulation line 20 of the compressor 12 according to the embodiment.
  • the compressor 12 includes a compressor main body 16, a compressor cooling system 22, and an oil circulation line 20 connecting these.
  • the compressor cooling system 22 includes a liquid-cooled heat exchanger 24 and an air-cooled heat exchanger 26, and is configured to cool the oil circulation line 20.
  • the liquid-cooled heat exchanger 24 and the air-cooled heat exchanger 26 are connected in series, and the liquid-cooled heat exchanger 24 is provided upstream of the air-cooled heat exchanger 26.
  • the oil circulation line 20 branches into a first oil line 46 and a second oil line 48 upstream of the air-cooled heat exchanger 26, that is, between the liquid-cooled heat exchanger 24 and the air-cooled heat exchanger 26.
  • the air-cooled heat exchanger 26 includes a cooling fan 50, and the first oil line 46 is forcibly cooled by the air flow generated within the air-cooled heat exchanger 26 when the cooling fan 50 operates.
  • the first oil line 46 and the second oil line 48 join together again downstream of the air-cooled heat exchanger 26, that is, between the air-cooled heat exchanger 26 and the oil inlet of the compressor body 16.
  • the second oil line 48 bypasses the air-cooled heat exchanger 26.
  • the second oil line 48 is provided outside the air-cooled heat exchanger 26 in the compressor 12 and does not pass through the air-cooled heat exchanger 26 .
  • the second oil line 48 may include an on-off valve 58 that closes when the cooling fan 50 is activated and opens when the cooling fan 50 is stopped. Therefore, the fan controller 54 may be configured to receive a sensor signal indicating a measurement result from at least one sensor, and operate the cooling fan 50 and the on-off valve 58 based on the measurement result. The fan controller 54 may operate the cooling fan 50 and close the on-off valve 58, or may stop the cooling fan 50 and open the on-off valve 58. Note that FIG. 3 shows, as an example, a case where a sensor signal from the second sensor 62 is input to the fan controller 54. As mentioned above, other sensors (eg, first sensor 61, or third sensor 63, or fourth sensor 64, or fifth sensor 65) may be used.
  • the on-off valve 58 is closed and the air-cooled heat exchanger 26 is operated to compensate for the cooling failure of the liquid-cooled heat exchanger 24 with the air-cooled heat exchanger 26. Can be replaced.
  • a plurality of oil lines may be provided in the air-cooled heat exchanger 26, and these oil lines may be cooled by the cooling fan 50, similarly to the examples of FIGS. 1 and 2.
  • the oil circulation line 20 branches into a first oil line 46 and a second oil line 48 at the air-cooled heat exchanger 26, but there are more oil lines, for example three or four. You may branch to
  • the liquid-cooled heat exchanger 24 and the air-cooled heat exchanger 26 are connected in series in the compressor cooling system 22, and the liquid-cooled heat exchanger 24 is provided upstream of the air-cooled heat exchanger 26.
  • the compressor cooling system 22 may have other configurations.
  • the liquid-cooled heat exchanger 24 and the air-cooled heat exchanger 26 may be connected in series, and the air-cooled heat exchanger 26 may be provided upstream of the liquid-cooled heat exchanger 24.
  • the liquid-cooled heat exchanger 24 and the air-cooled heat exchanger 26 may be connected in parallel.
  • the cooling fan 50 of the air-cooled heat exchanger 26 may generate an air flow in the opposite direction from the example described above, and may be configured to blow air into the air-cooled heat exchanger 26 from the outside. .
  • the cooling fan 50 may be configured to blow air onto the refrigerant gas line 18, the first oil line 46, and the second oil line 48.
  • the present invention can be used in the field of oil-lubricated compressors for cryogenic refrigerators.

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  • Compressor (AREA)

Abstract

Un compresseur (12) pour un cryoréfrigérateur (10) est pourvu : d'un échangeur de chaleur refroidi par air (26) pourvu d'un ventilateur de refroidissement (50) et d'une première conduite d'huile (46) disposée de façon à subir un refroidissement forcé par le ventilateur de refroidissement (50) ; et d'une seconde conduite d'huile (48) pour contourner la première conduite d'huile (46). La seconde conduite d'huile (48) peut être disposée de manière à subir le refroidissement forcé par le ventilateur de refroidissement (50).
PCT/JP2023/015355 2022-05-11 2023-04-17 Compresseur du type à lubrification par huile pour cryoréfrigérateur WO2023218865A1 (fr)

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JP2022078318A JP2023167267A (ja) 2022-05-11 2022-05-11 オイル潤滑式の極低温冷凍機用圧縮機
JP2022-078318 2022-05-11

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011099669A (ja) * 2009-11-09 2011-05-19 Sumitomo Heavy Ind Ltd 空冷ヘリウムコンプレッサ
US20170175743A1 (en) * 2015-12-18 2017-06-22 Sumitomo (Shi) Cryogenics Of America, Inc. Cold start helium compressor
JP2019505751A (ja) * 2015-12-18 2019-02-28 スミトモ （エスエイチアイ） クライオジェニックス オブ アメリカ インコーポレイテッドＳｕｍｉｔｏｍｏ（ＳＨＩ）Ｃｒｙｏｇｅｎｉｃｓ ｏｆ Ａｍｅｒｉｃａ，Ｉｎｃ． デュアル・アフタークーラー付きヘリウムコンプレッサ

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011099669A (ja) * 2009-11-09 2011-05-19 Sumitomo Heavy Ind Ltd 空冷ヘリウムコンプレッサ
US20170175743A1 (en) * 2015-12-18 2017-06-22 Sumitomo (Shi) Cryogenics Of America, Inc. Cold start helium compressor
JP2019505751A (ja) * 2015-12-18 2019-02-28 スミトモ （エスエイチアイ） クライオジェニックス オブ アメリカ インコーポレイテッドＳｕｍｉｔｏｍｏ（ＳＨＩ）Ｃｒｙｏｇｅｎｉｃｓ ｏｆ Ａｍｅｒｉｃａ，Ｉｎｃ． デュアル・アフタークーラー付きヘリウムコンプレッサ

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