JP6672056B2 - Turbo compressor, turbo refrigeration device provided with the same - Google Patents

Turbo compressor, turbo refrigeration device provided with the same Download PDF

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JP6672056B2
JP6672056B2 JP2016086202A JP2016086202A JP6672056B2 JP 6672056 B2 JP6672056 B2 JP 6672056B2 JP 2016086202 A JP2016086202 A JP 2016086202A JP 2016086202 A JP2016086202 A JP 2016086202A JP 6672056 B2 JP6672056 B2 JP 6672056B2
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refrigerant
bearing
liquid refrigerant
turbo compressor
auxiliary
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JP2017194042A (en
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長谷川　泰士
泰士 長谷川
真太郎 大村
真太郎 大村
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Mitsubishi Heavy Industries Thermal Systems Ltd
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Mitsubishi Heavy Industries Thermal Systems Ltd
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Priority to JP2016086202A priority Critical patent/JP6672056B2/en
Priority to US16/095,112 priority patent/US20190211834A1/en
Priority to CN201780038888.XA priority patent/CN109416049A/en
Priority to PCT/JP2017/015636 priority patent/WO2017183644A1/en
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    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/058—Bearings magnetic; electromagnetic
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/059—Roller bearings
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • 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
    • F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine 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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • F25B31/008—Cooling of compressor or motor by injecting a liquid

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Electromagnetism (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Rolling Contact Bearings (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
  • Mounting Of Bearings Or Others (AREA)

Description

本発明は、ターボ圧縮機、これを備えたターボ冷凍装置に関するものである。   The present invention relates to a turbo compressor and a turbo refrigeration apparatus provided with the turbo compressor.

地域冷暖房の熱源用等に使用されているターボ冷凍装置は、周知のように、電動機で駆動される遠心タービン型のターボ圧縮機を備えている。このようなターボ圧縮機において、特許文献１に開示されているように、ロータ軸の軸受として磁気軸受や気体軸受（エア軸受）等の非接触軸受を使用することにより、軸受における回転抵抗を無くすと同時に、軸受の潤滑を不要にしたものがある。非接触軸受は、軸受に対してロータ軸を浮上させながら支持するため、回転抵抗を非常に小さくすることができる。   As is well known, a centrifugal refrigeration apparatus used as a heat source for district cooling and heating includes a centrifugal turbine type turbo compressor driven by an electric motor. In such a turbo compressor, as disclosed in Patent Document 1, a non-contact bearing such as a magnetic bearing or a gas bearing (air bearing) is used as a rotor shaft bearing, thereby eliminating rotational resistance in the bearing. At the same time, some bearings do not require lubrication. Since the non-contact bearing supports the rotor shaft while floating with respect to the bearing, the rotation resistance can be extremely reduced.

この場合、停電等により電源が遮断されて非接触軸受の機能が停止した時に、非接触軸受に代わってロータ軸を支持する補助軸受（タッチダウン軸受）が設けられる。この補助軸受としては転がり軸受が用いられる。補助軸受のラジアル方向の隙間は非接触軸受よりも小さく設定されているため、電源遮断時においてロータ軸は非接触軸受に接触するよりも先に補助軸受によって支持（タッチダウン）され、非接触軸受の破損が防止される。   In this case, when the power supply is cut off due to a power failure or the like and the function of the non-contact bearing stops, an auxiliary bearing (touch-down bearing) that supports the rotor shaft is provided instead of the non-contact bearing. A rolling bearing is used as the auxiliary bearing. Since the gap in the radial direction of the auxiliary bearing is set smaller than that of the non-contact bearing, the rotor shaft is supported (touched down) by the auxiliary bearing before contacting the non-contact bearing when the power is cut off, and the non-contact bearing Is prevented from being damaged.

特開２００２−２１８７０８号公報JP 2002-218708 A

補助軸受としては、一般に転がり軸受が採用されるが、非接触軸受が潤滑や冷却を必要としないため、潤滑油系統は付設されず、転がり軸受である補助軸受はグリス潤滑もしくは無潤滑となるケースが多い。
このため、補助軸受の軸受寿命が短くなる、あるいはタッチダウン回数が限定されてしまうという課題があった。これを防止するためには補助軸受の材質として特殊鋼を採用したり、内外輪や転動部材に特殊な表面処理を施したりする必要があり、軸受システムとして高価格となってしまう。 Rolling bearings are generally used as auxiliary bearings.However, since non-contact bearings do not require lubrication or cooling, no lubricating oil system is provided and auxiliary bearings that are rolling bearings are grease lubricated or non-lubricated. There are many.
For this reason, there is a problem that the bearing life of the auxiliary bearing is shortened or the number of touchdowns is limited. In order to prevent this, it is necessary to use special steel as the material of the auxiliary bearing, or to apply a special surface treatment to the inner and outer rings and the rolling members, resulting in a high price as a bearing system.

本発明は、このような事情に鑑みてなされたものであり、ロータ軸を支持する非接触軸受に隣接して設けられる、タッチダウン用の補助軸受の低コスト化および長寿命化を図ることができるターボ圧縮機、これを備えたターボ冷凍装置を提供することを目的とする。   The present invention has been made in view of such circumstances, and aims to reduce the cost and extend the life of an auxiliary bearing for touchdown provided adjacent to a non-contact bearing that supports a rotor shaft. It is an object of the present invention to provide a turbo compressor that can be used and a turbo refrigeration apparatus including the turbo compressor.

上記課題を解決するために、本発明は、以下の手段を採用する。
本発明の第１態様に係るターボ圧縮機は、ロータ軸と、前記ロータ軸の中間部に同軸的に設けられて前記ロータ軸を回転駆動する電動機と、前記ロータ軸の一端に固定されて冷媒を圧縮する冷媒圧縮部を構成するインペラと、前記電動機と前記インペラとの間、および前記ロータ軸の他端を軸支する非接触軸受と、前記非接触軸受に隣接し、該非接触軸受の機能停止時に該非接触軸受に代わって前記ロータ軸を軸支する補助軸受と、前記非接触軸受の機能停止時に、前記補助軸受の内部に前記冷媒を潤滑剤として供給する潤滑冷媒供給部と、を備えたものである。 In order to solve the above problems, the present invention employs the following solutions.
A turbo compressor according to a first aspect of the present invention includes a rotor shaft, an electric motor provided coaxially at an intermediate portion of the rotor shaft to rotationally drive the rotor shaft, and a refrigerant fixed to one end of the rotor shaft. An impeller that constitutes a refrigerant compression unit that compresses a non-contact bearing that supports the other end of the rotor shaft between the electric motor and the impeller; and a function of the non-contact bearing that is adjacent to the non-contact bearing. An auxiliary bearing that supports the rotor shaft in place of the non-contact bearing when stopped, and a lubricating refrigerant supply unit that supplies the refrigerant as a lubricant inside the auxiliary bearing when the non-contact bearing stops functioning. It is a thing.

上記構成のターボ圧縮機によれば、停電等により電源が遮断されて非接触軸受の機能が停止した時には、非接触軸受に代わって補助軸受がロータ軸を支持し、これと同時に潤滑冷媒供給部によって補助軸受の内部に冷媒が潤滑剤として供給される。このため、補助軸受の潤滑状態を向上させることができ、特殊で高価な軸受を用いることなく在来の軸受を使用可能とし、補助軸受の低コスト化および長寿命化を図ることができる。   According to the turbo compressor having the above configuration, when the power is cut off due to a power failure or the like and the function of the non-contact bearing stops, the auxiliary bearing supports the rotor shaft instead of the non-contact bearing, and at the same time, the lubricating refrigerant supply unit As a result, a coolant is supplied as a lubricant into the auxiliary bearing. Therefore, the lubrication state of the auxiliary bearing can be improved, a conventional bearing can be used without using a special and expensive bearing, and the cost and the life of the auxiliary bearing can be reduced.

前記構成において、前記潤滑冷媒供給部は、液相状の前記冷媒が貯留された液冷媒貯留部と、前記補助軸受と前記液冷媒貯留部との間を接続する液冷媒供給通路と、前記液冷媒供給通路に接続され、通電された状態で閉となる電磁弁と、を備えた構成としてもよい。   In the above configuration, the lubricating refrigerant supply section includes a liquid refrigerant storage section in which the liquid-phase refrigerant is stored, a liquid refrigerant supply passage connecting between the auxiliary bearing and the liquid refrigerant storage section, A solenoid valve connected to the coolant supply passage and closed when energized.

上記構成とすれば、電源遮断時において、通電された状態で閉となる電磁弁が開く。このため、液冷媒貯留部に貯留されている液相状の冷媒が、液冷媒供給通路を経て補助軸受に供給される。本構成によれば、制御部を設けることなく電源遮断時に電磁弁を開いて冷媒を補助軸受に供給することができ、軸受システムを低コスト化することができる。   With this configuration, when the power is cut off, the solenoid valve that is closed when energized is opened. For this reason, the liquid-phase refrigerant stored in the liquid refrigerant storage section is supplied to the auxiliary bearing via the liquid refrigerant supply passage. According to this configuration, the coolant can be supplied to the auxiliary bearing by opening the solenoid valve when the power is cut off without providing the control unit, and the cost of the bearing system can be reduced.

前記構成において、前記液冷媒貯留部は、前記冷媒圧縮部により圧縮された前記冷媒が凝縮される凝縮器の底部としてもよい。凝縮器の底部には、圧縮および凝縮された液相状の冷媒が貯留されており、この液相状の冷媒の圧力は補助軸受の周辺圧力よりも高いため、電磁弁が開くと同時に圧力差によって冷媒が補助軸受に迅速に供給される。このため、電源遮断時に素早く冷媒を補助軸受に供給して潤滑し、補助軸受の長寿命化を図ることができる。   In the above configuration, the liquid refrigerant storage section may be a bottom portion of a condenser in which the refrigerant compressed by the refrigerant compression section is condensed. At the bottom of the condenser, compressed and condensed liquid-phase refrigerant is stored, and the pressure of the liquid-phase refrigerant is higher than the peripheral pressure of the auxiliary bearing. The refrigerant is quickly supplied to the auxiliary bearing. Therefore, when the power is shut off, the coolant is quickly supplied to the auxiliary bearing to lubricate it, and the life of the auxiliary bearing can be extended.

前記構成において、前記液冷媒貯留部は、前記電動機を収容するケーシングに設けられた、前記電動機冷却用の液冷媒ジャケットとしてもよい。この液冷媒ジャケットは、補助軸受の近傍に位置するとともに、その内部に圧縮および凝縮された液相状の冷媒が循環している。このため、電源遮断時に電磁弁が開くと同時に、圧力差、または重力によって液冷媒ジャケットの冷媒を補助軸受に容易に供給することができる。本構成によれば、ターボ圧縮機と周辺の機器類との間を液冷媒供給通路で接続する必要がないため、軸受システムを簡素化することができる。   The said structure WHEREIN: The said liquid refrigerant | coolant storage part is good also as a liquid refrigerant jacket for the said electric motor cooling provided in the casing which accommodates the said electric motor. The liquid refrigerant jacket is located near the auxiliary bearing, and circulates therein a compressed and condensed liquid refrigerant. Therefore, at the same time when the electromagnetic valve is opened when the power is turned off, the refrigerant in the liquid refrigerant jacket can be easily supplied to the auxiliary bearing by the pressure difference or the gravity. According to this configuration, it is not necessary to connect the turbo compressor and peripheral devices with the liquid refrigerant supply passage, so that the bearing system can be simplified.

前記構成において、前記液冷媒貯留部は、液相状の前記冷媒を、前記補助軸受の周辺圧力よりも高い圧力を付与しながら貯留する圧力付与容器としてもよい。こうすれば、電源遮断時に電磁弁が開くと同時に、圧力差によって圧力付与容器の冷媒が補助軸受に供給される。本構成によれば、ターボ圧縮機により圧縮された冷媒を抽出する系統を設ける必要がないため、軸受システムを簡素化することができる。また、冷凍装置の運転状態によらず、潤滑用冷媒供給圧力を必要規定値以上に保持することができ、潤滑用冷媒を確実に供給することができる。   In the above configuration, the liquid refrigerant storage section may be a pressure application container that stores the liquid-phase refrigerant while applying a pressure higher than a peripheral pressure of the auxiliary bearing. With this configuration, when the power supply is cut off, the refrigerant in the pressure applying container is supplied to the auxiliary bearing by the pressure difference at the same time as the solenoid valve is opened. According to this configuration, since it is not necessary to provide a system for extracting the refrigerant compressed by the turbo compressor, the bearing system can be simplified. Further, the lubricating refrigerant supply pressure can be maintained at a required specified value or more irrespective of the operation state of the refrigeration apparatus, and the lubricating refrigerant can be reliably supplied.

前記構成において、補助軸受を転がり軸受とし、その外輪、内輪、および転動体の少なくともいずれかの材質としてセラミック材を採用してもよい。セラミック材は熱膨張量が小さく、補助軸受の温度変化時における軸受隙間の変化量を小さくすることができるため、冷媒のように低粘度の流体でも補助軸受を良好に潤滑することができる。   In the above configuration, the auxiliary bearing may be a rolling bearing, and a ceramic material may be employed as a material of at least one of the outer ring, the inner ring, and the rolling element. Since the ceramic material has a small amount of thermal expansion and can reduce the amount of change in the bearing gap when the temperature of the auxiliary bearing changes, the auxiliary bearing can be satisfactorily lubricated even with a low-viscosity fluid such as a refrigerant.

前記構成において、補助軸受を転がり軸受とし、その外輪、内輪、および転動体の少なくともいずれかの材質として、低粘度流体による潤滑でも潤滑膜が形成される材質を採用してもよい。これにより、冷媒のように低粘度の流体でも補助軸受を良好に潤滑することができる。   In the above configuration, the auxiliary bearing may be a rolling bearing, and a material that forms a lubricating film even with lubrication with a low-viscosity fluid may be used as at least one of the outer ring, the inner ring, and the rolling element. This makes it possible to satisfactorily lubricate the auxiliary bearing even with a low-viscosity fluid such as a refrigerant.

前記構成において、補助軸受を転がり軸受とし、その外輪、内輪、および転動体の少なくともいずれかにダイヤモンドライクカーボンをコーティングしてもよい。ダイヤモンドライクカーボンは、低粘度流体による潤滑でも潤滑膜が形成されるため、冷媒のように低粘度の流体でも補助軸受を良好に潤滑することができる。   In the above configuration, the auxiliary bearing may be a rolling bearing, and at least one of the outer ring, the inner ring, and the rolling element may be coated with diamond-like carbon. Since diamond-like carbon forms a lubricating film even when lubricated with a low-viscosity fluid, the auxiliary bearing can be satisfactorily lubricated even with a low-viscosity fluid such as a refrigerant.

本発明の第２態様に係るターボ冷凍装置は、上記のいずれかに記載のターボ圧縮機と、前記ターボ圧縮機によって圧縮された前記冷媒を凝縮させる凝縮器と、凝縮した前記冷媒を蒸発させる蒸発器と、を具備してなるものであり、これによって上記の各作用および効果が奏される。   A turbo refrigeration apparatus according to a second aspect of the present invention includes a turbo compressor according to any one of the above, a condenser that condenses the refrigerant compressed by the turbo compressor, and an evaporator that evaporates the condensed refrigerant. And a container, whereby the above-described respective operations and effects are achieved.

以上のように、本発明に係るターボ圧縮機、これを備えたターボ冷凍装置によれば、ターボ圧縮機のロータ軸を支持する非接触軸受に隣接して設けられる、タッチダウン用の補助軸受の低コスト化と長寿命化とを両立させることができる。   As described above, according to the turbo compressor according to the present invention, the turbo refrigeration apparatus including the turbo compressor, the auxiliary bearing for touchdown provided adjacent to the non-contact bearing supporting the rotor shaft of the turbo compressor. Low cost and long life can both be achieved.

本発明の第１実施形態を示すターボ冷凍装置の全体図である。1 is an overall view of a turbo refrigeration apparatus showing a first embodiment of the present invention. 図１に示すターボ圧縮機の拡大縦断面図である。FIG. 2 is an enlarged vertical sectional view of the turbo compressor shown in FIG. 1. 本発明の第２実施形態を示すターボ圧縮機の拡大縦断面図である。It is an expansion longitudinal section of a turbo compressor showing a 2nd embodiment of the present invention. 本発明の第３実施形態を示すターボ冷凍装置の全体図である。It is the whole turbo refrigeration equipment figure showing a 3rd embodiment of the present invention.

以下に、本発明の複数の実施形態について図面を参照しながら説明する。
［第１実施形態］
図１は、本発明の第１実施形態を示すターボ冷凍装置の全体図である。このターボ冷凍装置１は、冷媒を圧縮するターボ圧縮機２と、凝縮器３と、膨張弁４と、蒸発器５とを備えて構成されている。ターボ圧縮機２の冷媒圧縮部７と凝縮器３との間が吐出管８で接続され、凝縮器３と蒸発器５との間が冷媒管９で接続され、蒸発器５とターボ圧縮機２（冷媒圧縮部７）との間が吸入管１０で接続されている。膨張弁４は冷媒管９に接続されている。 Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings.
[First Embodiment]
FIG. 1 is an overall view of a turbo refrigeration apparatus showing a first embodiment of the present invention. The turbo refrigeration apparatus 1 includes a turbo compressor 2 for compressing a refrigerant, a condenser 3, an expansion valve 4, and an evaporator 5. The refrigerant compressor 7 of the turbo compressor 2 and the condenser 3 are connected by a discharge pipe 8, the condenser 3 and the evaporator 5 are connected by a refrigerant pipe 9, and the evaporator 5 and the turbo compressor 2 are connected. (The refrigerant compression section 7) is connected with the suction pipe 10. The expansion valve 4 is connected to a refrigerant pipe 9.

このターボ冷凍装置１において、ターボ圧縮機２（冷媒圧縮部７）により圧縮された冷媒は吐出管８を経て凝縮器３に送給され、ここで冷却水と熱交換されることにより凝縮熱を冷却されて凝縮される。凝縮器３で加熱された冷却水は暖房空調等に利用される。   In this turbo refrigeration apparatus 1, the refrigerant compressed by the turbo compressor 2 (refrigerant compression section 7) is sent to the condenser 3 via the discharge pipe 8, where the refrigerant exchanges heat with the cooling water to generate heat of condensation. Cooled and condensed. The cooling water heated by the condenser 3 is used for heating air conditioning and the like.

凝縮器３にて凝縮された冷媒は、冷媒管９に設けられた膨張弁４を通過することにより断熱膨張して蒸発器５に給送される。蒸発器５の内部では、膨張弁４において断熱膨張した低温の冷媒が水と熱交換され、ここで冷却された冷水は冷房空調や工業用冷却水等として利用される。そして、冷却水との熱交換により気化した冷媒は吸入管１０を経て再びターボ圧縮機２（冷媒圧縮部７）に吸入されて圧縮され、以下、このサイクルが繰り返される。   The refrigerant condensed in the condenser 3 is adiabatically expanded by passing through the expansion valve 4 provided in the refrigerant pipe 9 and is supplied to the evaporator 5. Inside the evaporator 5, the low-temperature refrigerant adiabatically expanded in the expansion valve 4 exchanges heat with water, and the cold water cooled here is used as cooling air conditioning, industrial cooling water, or the like. Then, the refrigerant vaporized by heat exchange with the cooling water is sucked into the turbo compressor 2 (refrigerant compression unit 7) again through the suction pipe 10 and compressed, and the cycle is repeated thereafter.

図２にも示すように、ターボ圧縮機２は、その外殻を形成するケーシング１３と、電動機１４と、ロータ軸１５と、冷媒圧縮部７を構成するインペラ１６と、一対の主軸受１８ａ，１８ｂと、これらの主軸受１８ａ，１８ｂに隣接して設けられた一対の補助軸受１９ａ，１９ｂと、スラスト軸受２０ａ，２０ｂとを具備して構成されている。ケーシング１３の内部は隔壁１３ａによって電動機室１３Ａと圧縮室１３Ｂとに区画されており、電動機室１３Ａに電動機１４が収容され、圧縮室１３Ｂに冷媒圧縮部７（インペラ１６）が収容されている。   As shown in FIG. 2, the turbo compressor 2 has a casing 13 forming an outer shell, an electric motor 14, a rotor shaft 15, an impeller 16 forming a refrigerant compression unit 7, and a pair of main bearings 18 a, 18b, a pair of auxiliary bearings 19a, 19b provided adjacent to the main bearings 18a, 18b, and thrust bearings 20a, 20b. The interior of the casing 13 is divided into a motor chamber 13A and a compression chamber 13B by a partition 13a. The motor chamber 13A houses the electric motor 14, and the compression chamber 13B houses the refrigerant compressor 7 (impeller 16).

電動機１４は、ケーシング１３側に固定されたステータ１４ａと、ロータ軸１５に固定されてステータ１４ａの内部で回転するロータ１４ｂとを備えて構成されている。ロータ軸１５の一端は隔壁１３ａを貫通して圧縮室１３Ｂに突入しており、ここにインペラ１６が一体回転するように設けられて冷媒圧縮部７が構成されている。   The electric motor 14 includes a stator 14a fixed to the casing 13 side, and a rotor 14b fixed to the rotor shaft 15 and rotating inside the stator 14a. One end of the rotor shaft 15 penetrates through the partition wall 13a and protrudes into the compression chamber 13B, where the impeller 16 is provided so as to rotate integrally, and the refrigerant compression section 7 is configured.

一対の主軸受１８ａ，１８ｂは、その一方（１８ａ）が電動機１４とインペラ１６との間を軸支し、他方（１８ｂ）がロータ軸１５の他端（反インペラ１６側の端部）を軸支している。これらの主軸受１８ａ，１８ｂとしては、磁気軸受や気体軸受（エア軸受）等、公知の非接触軸受が用いられており、これによって回転抵抗の低減と無潤滑化が図られている。   One (18a) of the pair of main bearings 18a and 18b supports the shaft between the electric motor 14 and the impeller 16, and the other (18b) supports the other end (the end on the side opposite to the impeller 16) of the rotor shaft 15. Support. Known non-contact bearings, such as magnetic bearings and gas bearings (air bearings), are used as the main bearings 18a and 18b, thereby reducing rotational resistance and achieving lubrication-free.

主軸受１８ａ，１８ｂに隣接して設けられている一対の補助軸受１９ａ，１９ｂは転がり軸受であり、停電時等の電源遮断時における主軸受１８ａ，１８ｂの機能停止時に、主軸受１８ａ，１８ｂに代わってロータ軸１５を軸支する、いわゆるタッチダウン軸受である。この補助軸受１９ａ，１９ｂの軸受隙間は、主軸受１８ａ，１８ｂの軸受隙間に対し、例えば半分程度と、十分に狭く設計されている。このため、主軸受１８ａ，１８ｂの機能が停止して補助軸受１９ａ，１９ｂがロータ軸１５を支持する時でも主軸受１８ａ，１８ｂの軸受隙間が残され、主軸受１８ａ，１８ｂの破損が回避される。   A pair of auxiliary bearings 19a, 19b provided adjacent to the main bearings 18a, 18b are rolling bearings, which are connected to the main bearings 18a, 18b when the main bearings 18a, 18b stop functioning at the time of power interruption such as a power failure. Instead, it is a so-called touch-down bearing that supports the rotor shaft 15. The bearing gap between the auxiliary bearings 19a and 19b is designed to be sufficiently narrow, for example, about half of the bearing gap between the main bearings 18a and 18b. For this reason, even when the functions of the main bearings 18a and 18b stop and the auxiliary bearings 19a and 19b support the rotor shaft 15, a bearing gap between the main bearings 18a and 18b is left, and damage to the main bearings 18a and 18b is avoided. You.

スラスト軸受２０ａ，２０ｂは、ロータ軸１５の他端側先端に設けられた円板状のスラストプレート１５ａを挟んで設けられており、ロータ軸１５の軸方向への動きを規制している。このスラスト軸受２０ａ，２０ｂは、主軸受１８ａ，１８ｂと同じく非接触軸受とされている。   The thrust bearings 20a and 20b are provided so as to sandwich a disk-shaped thrust plate 15a provided at the other end of the rotor shaft 15, and regulate the axial movement of the rotor shaft 15. The thrust bearings 20a and 20b are non-contact bearings, like the main bearings 18a and 18b.

図１、図２に示すように、ターボ圧縮機２には潤滑冷媒供給部２５が備えられている。この潤滑冷媒供給部２５は、停電等により電源が遮断されて非接触軸受である主軸受１８ａ，１８ｂの機能が停止した時に、上述のように主軸受１８ａ，１８ｂに代わってロータ軸１５を支持する転がり軸受である補助軸受１９ａ，１９ｂの内部に冷媒を潤滑剤として供給するものである。潤滑冷媒供給部２５は、液相状の冷媒Ｒが貯留された液冷媒貯留部２６と、この液冷媒貯留部２６と補助軸受１９ａ，１９ｂとの間を接続する液冷媒供給通路２７と、液冷媒供給通路２７に接続された電磁弁２８とを備えている。   As shown in FIGS. 1 and 2, the turbo compressor 2 is provided with a lubricating refrigerant supply unit 25. The lubricating refrigerant supply unit 25 supports the rotor shaft 15 instead of the main bearings 18a and 18b as described above when the power is cut off due to a power failure or the like and the functions of the non-contact bearings 18a and 18b are stopped. The refrigerant is supplied as a lubricant into the auxiliary bearings 19a and 19b, which are rolling bearings. The lubricating refrigerant supply unit 25 includes a liquid refrigerant storage unit 26 in which the liquid refrigerant R is stored, a liquid refrigerant supply passage 27 that connects the liquid refrigerant storage unit 26 and the auxiliary bearings 19a and 19b, An electromagnetic valve 28 connected to the refrigerant supply passage 27.

本実施形態において、液冷媒貯留部２６として凝縮器３の底部が利用されている。凝縮器３の底部には圧縮および凝縮された液相状の冷媒Ｒが常に貯留されており、この液相状の冷媒Ｒの液面よりも低い位置に液冷媒供給通路２７の一端が接続されている。液冷媒供給通路２７の他端は２本の分岐通路２７ａ，２７ｂに分岐しており、一方の分岐通路２７ａが一方の補助軸受１９ａに接続され、他方の分岐通路２７ｂが他方の補助軸受１９ｂに接続されている。電磁弁２８は、液冷媒供給通路２７の分岐前の区間に接続されている。この電磁弁２８は、通電された状態で閉となる、即ちノーマルオープン形式である。   In the present embodiment, the bottom of the condenser 3 is used as the liquid refrigerant storage unit 26. The compressed and condensed liquid refrigerant R is always stored at the bottom of the condenser 3, and one end of the liquid refrigerant supply passage 27 is connected to a position lower than the liquid surface of the liquid refrigerant R. ing. The other end of the liquid refrigerant supply passage 27 branches into two branch passages 27a and 27b. One branch passage 27a is connected to one auxiliary bearing 19a, and the other branch passage 27b is connected to the other auxiliary bearing 19b. It is connected. The solenoid valve 28 is connected to a section of the liquid refrigerant supply passage 27 before branching. The solenoid valve 28 is closed when energized, that is, of a normally open type.

以上のように構成されたターボ冷凍装置１およびターボ圧縮機２において、停電等により電源が遮断された場合には、非接触軸受である主軸受１８ａ，１８ｂの機能が停止する。このため、主軸受１８ａ，１８ｂに代わって補助軸受１９ａ，１９ｂがロータ軸１５を支持する。これと同時に、通電された状態で閉となる電磁弁２８が、電源が遮断されたことによって開かれる。   In the turbo refrigeration apparatus 1 and the turbo compressor 2 configured as described above, when the power is cut off due to a power failure or the like, the functions of the main bearings 18a and 18b, which are non-contact bearings, stop. For this reason, the auxiliary bearings 19a and 19b support the rotor shaft 15 instead of the main bearings 18a and 18b. At the same time, the solenoid valve 28 that closes when energized is opened when the power is cut off.

凝縮器３の底部にある液冷媒貯留部２６に貯留された液相状の冷媒Ｒは、その圧力が補助軸受１９ａ，１９ｂの周辺圧力（ケーシング１３の内部圧力）よりも高いため、電磁弁２８が開くと同時に圧力差により液冷媒供給通路２７（分岐通路２７ａ，２７ｂ）を経て補助軸受１９ａ，１９ｂに供給される。このため、補助軸受１９ａ，１９ｂの内部に液相状の冷媒Ｒが潤滑剤として供給され、補助軸受１９ａ，１９ｂが潤滑、冷却される。   Since the pressure of the liquid refrigerant R stored in the liquid refrigerant storage section 26 at the bottom of the condenser 3 is higher than the peripheral pressure of the auxiliary bearings 19a and 19b (the internal pressure of the casing 13), the electromagnetic valve 28 Is opened, and is supplied to the auxiliary bearings 19a and 19b via the liquid refrigerant supply passage 27 (branch passages 27a and 27b) due to the pressure difference. Therefore, the liquid refrigerant R is supplied as a lubricant into the auxiliary bearings 19a and 19b, and the auxiliary bearings 19a and 19b are lubricated and cooled.

上記の通り、このターボ圧縮機２は、非接触軸受である主軸受１８ａ，１８ｂの機能停止時に、これに代わってロータ軸１５を支持する補助軸受１９ａ，１９ｂの内部に液相状の冷媒Ｒを潤滑剤として供給する潤滑冷媒供給部２５を備えている。これにより、電源遮断時における補助軸受１９ａ，１９ｂの潤滑状態を向上させることができ、特殊で高価な軸受を用いることなく在来の軸受を使用可能とし、補助軸受１９ａ，１９ｂの低コスト化と長寿命化とを両立させることができる。   As described above, when the main bearings 18a, 18b, which are non-contact bearings, stop functioning, the turbo compressor 2 replaces the liquid refrigerant R inside the auxiliary bearings 19a, 19b supporting the rotor shaft 15. Is provided as a lubricant. This makes it possible to improve the lubrication state of the auxiliary bearings 19a and 19b when the power is cut off, to enable the use of conventional bearings without using special and expensive bearings, to reduce the cost of the auxiliary bearings 19a and 19b, and to reduce the cost. Long life can be achieved at the same time.

電源遮断時に液冷媒供給通路２７を開く電磁弁２８として、通電された状態で閉となるノーマルオープンの電磁弁を採用したことにより、専用の制御部を設けることなく電源遮断時に電磁弁２８を開かせて冷媒Ｒを補助軸受１９ａ，１９ｂに供給することができる。このため、軸受システムとしての低コスト化を図ることができる。   A normally open solenoid valve that closes when energized is used as the solenoid valve 28 that opens the liquid refrigerant supply passage 27 when the power is shut off, so that the solenoid valve 28 opens when the power is shut off without providing a dedicated control unit. Thus, the refrigerant R can be supplied to the auxiliary bearings 19a and 19b. For this reason, cost reduction as a bearing system can be achieved.

補助軸受１９ａ，１９ｂの内部に潤滑剤として供給される液相状の冷媒Ｒの供給源である液冷媒貯留部２６は凝縮器３の底部となっている。凝縮器３の底部には、圧縮および凝縮された液相状の冷媒Ｒが貯留されており、この液相状の冷媒Ｒの圧力は補助軸受１９ａ，１９ｂの周辺圧力よりも高いため、電磁弁２８が開くと同時に圧力差によって冷媒Ｒが補助軸受１９ａ，１９ｂに迅速に供給される。このため、電源遮断時に素早く冷媒Ｒを補助軸受１９ａ，１９ｂに供給して潤滑し、補助軸受１９ａ，１９ｂの長寿命化を図ることができる。   The liquid refrigerant reservoir 26 serving as a supply source of the liquid refrigerant R supplied as a lubricant into the auxiliary bearings 19a and 19b is located at the bottom of the condenser 3. A compressed and condensed liquid-phase refrigerant R is stored at the bottom of the condenser 3. The pressure of the liquid-phase refrigerant R is higher than the peripheral pressure of the auxiliary bearings 19a and 19b. As soon as 28 opens, the refrigerant R is quickly supplied to the auxiliary bearings 19a, 19b by the pressure difference. Therefore, when the power is shut off, the coolant R is quickly supplied to the auxiliary bearings 19a and 19b to lubricate them, and the life of the auxiliary bearings 19a and 19b can be extended.

ところで、転がり軸受である補助軸受１９ａ，１９ｂの外輪、内輪、および転動体の少なくともいずれかの材質としてセラミック材を採用してもよい。セラミック材は熱膨張量が小さく、補助軸受１９ａ，１９ｂの温度変化時における軸受隙間の変化量を小さくすることができるため、液相状の冷媒Ｒのように低粘度の流体でも補助軸受１９ａ，１９ｂを良好に潤滑することができる。   By the way, a ceramic material may be adopted as a material of at least one of the outer ring, the inner ring, and the rolling elements of the auxiliary bearings 19a and 19b, which are rolling bearings. Since the ceramic material has a small amount of thermal expansion and can reduce the amount of change in the bearing gap when the temperature of the auxiliary bearings 19a and 19b changes, the auxiliary bearings 19a and 19b can be used even with a low-viscosity fluid such as a liquid refrigerant R. 19b can be satisfactorily lubricated.

また、補助軸受１９ａ，１９ｂの外輪、内輪、および転動体の少なくともいずれかの材質として、低粘度流体による潤滑でも潤滑膜が形成されやすい材質を採用したり、ダイヤモンドライクカーボン等の材質を外輪、内輪、転動体にコーティングしてもよい。これにより、液相状の冷媒Ｒのように低粘度の流体でも補助軸受１９ａ，１９ｂを良好に潤滑することができる。   In addition, as a material of at least one of the outer ring, the inner ring, and the rolling elements of the auxiliary bearings 19a and 19b, a material that easily forms a lubricating film even when lubricated with a low-viscosity fluid is used. The inner ring and rolling elements may be coated. Thus, the auxiliary bearings 19a and 19b can be satisfactorily lubricated even with a low-viscosity fluid such as the liquid refrigerant R.

［第２実施形態］
図３は、本発明の第２実施形態を示すターボ圧縮機２Ａの拡大縦断面図である。このターボ圧縮機２Ａは、そのケーシング１３の軸方向中間部分に、周方向に沿う液冷媒ジャケット３１が形成されている点において第１実施形態のターボ圧縮機２と相違する。この液冷媒ジャケット３１は、本来は電動機１４（ステータ１４ａ）を冷却するためのものであり、ここには圧縮および凝縮されて冷却された低温な液相状の冷媒Ｒが循環している。それ以外の構成は第１実施形態のターボ圧縮機２と同一であるため、各部に同一符号を付して説明は省略する。 [Second embodiment]
FIG. 3 is an enlarged vertical sectional view of a turbo compressor 2A showing a second embodiment of the present invention. The turbo compressor 2A differs from the turbo compressor 2 of the first embodiment in that a liquid refrigerant jacket 31 extending in the circumferential direction is formed at an axially intermediate portion of a casing 13 thereof. The liquid refrigerant jacket 31 is originally for cooling the electric motor 14 (stator 14a), and a low-temperature liquid-phase refrigerant R that has been compressed and condensed and cooled is circulated. Other configurations are the same as those of the turbo compressor 2 according to the first embodiment.

このターボ圧縮機２Ａにおいても、停電等により電源が遮断されて非接触軸受である主軸受１８ａ，１８ｂの機能が停止した場合には、主軸受１８ａ，１８ｂに代わって補助軸受１９ａ，１９ｂがロータ軸１５を支持する。そして、この補助軸受１９ａ，１９ｂの内部に冷媒を潤滑剤として供給する潤滑冷媒供給部３２が設けられている。この潤滑冷媒供給部３２においては、液相状の冷媒Ｒが貯留される液冷媒貯留部３３として液冷媒ジャケット３１が利用されている。   Also in the turbo compressor 2A, when the power is cut off due to a power failure or the like and the functions of the non-contact main bearings 18a and 18b are stopped, the auxiliary bearings 19a and 19b are replaced with the rotors 19a and 19b instead of the main bearings 18a and 18b. The shaft 15 is supported. Further, a lubricating refrigerant supply unit 32 for supplying a refrigerant as a lubricant is provided inside the auxiliary bearings 19a and 19b. In the lubricating refrigerant supply unit 32, a liquid refrigerant jacket 31 is used as a liquid refrigerant storage unit 33 in which a liquid refrigerant R is stored.

さらに、この潤滑冷媒供給部３２は、液冷媒ジャケット３１と補助軸受１９ａ，１９ｂとの間を接続する一対の液冷媒供給通路３４ａ，３４ｂと、この液冷媒供給通路３４ａ，３４ｂの各々に接続された電磁弁３５ａ，３５ｂとを備えている。電磁弁３５ａ，３５ｂは、第１実施形態における電磁弁２８を同じく通電された状態で閉となるノーマルオープン形式である。   Further, the lubricating refrigerant supply unit 32 is connected to a pair of liquid refrigerant supply passages 34a and 34b connecting between the liquid refrigerant jacket 31 and the auxiliary bearings 19a and 19b, and to each of the liquid refrigerant supply passages 34a and 34b. And solenoid valves 35a and 35b. The solenoid valves 35a and 35b are of a normally open type in which the solenoid valve 28 of the first embodiment is closed when the solenoid valve 28 is also energized.

以上のように構成されたターボ圧縮機２Ａにおいて、停電等により電源が遮断された場合には、非接触軸受である主軸受１８ａ，１８ｂの機能が停止し、これに代わって補助軸受１９ａ，１９ｂがロータ軸１５を支持する。それと同時に、通電された状態で閉となる電磁弁３５ａ，３５ｂが、電源が遮断されたことによって開かれる。したがって、液冷媒ジャケット３１に貯留されている液相状の冷媒Ｒが、圧力差、または重力により、液冷媒供給通路３４ａ，３４ｂを経て補助軸受１９ａ，１９ｂに供給される。このため、補助軸受１９ａ，１９ｂの内部に液相状の冷媒Ｒが潤滑剤として供給され、補助軸受１９ａ，１９ｂが潤滑、冷却される。   In the turbo compressor 2A configured as described above, when the power is cut off due to a power failure or the like, the functions of the main bearings 18a and 18b, which are non-contact bearings, stop, and instead, the auxiliary bearings 19a and 19b are replaced. Support the rotor shaft 15. At the same time, the solenoid valves 35a and 35b that are closed when energized are opened when the power is cut off. Therefore, the liquid refrigerant R stored in the liquid refrigerant jacket 31 is supplied to the auxiliary bearings 19a and 19b via the liquid refrigerant supply passages 34a and 34b by a pressure difference or gravity. Therefore, the liquid refrigerant R is supplied as a lubricant into the auxiliary bearings 19a and 19b, and the auxiliary bearings 19a and 19b are lubricated and cooled.

このターボ圧縮機２Ａでは、潤滑冷媒供給部３２の液冷媒貯留部３３として液冷媒ジャケット３１が利用されており、この液冷媒ジャケット３１は、補助軸受１９ａ，１９ｂの近傍に位置するとともに、その内部に圧縮および凝縮された液相状の冷媒Ｒが循環している。このため、電源遮断時に電磁弁３５ａ，３５ｂが開かれると同時に、液冷媒ジャケット３１の冷媒Ｒを補助軸受１９ａ，１９ｂに容易に供給することができる。本構成によれば、ターボ圧縮機２Ａと周辺の機器類との間を冷媒供給通路で接続する必要がないため、軸受システムを簡素化することができる。   In the turbo compressor 2A, a liquid refrigerant jacket 31 is used as a liquid refrigerant storage section 33 of a lubricating refrigerant supply section 32. The liquid refrigerant jacket 31 is located near the auxiliary bearings 19a and 19b and has an internal structure. The refrigerant R in the liquid phase compressed and condensed is circulated. Therefore, when the power is cut off, the electromagnetic valves 35a and 35b are opened, and at the same time, the refrigerant R in the liquid refrigerant jacket 31 can be easily supplied to the auxiliary bearings 19a and 19b. According to this configuration, it is not necessary to connect the turbo compressor 2A and the peripheral devices with the refrigerant supply passage, so that the bearing system can be simplified.

［第３実施形態］
図４は、本発明の第３実施形態を示すターボ冷凍装置の全体図である。このターボ冷凍装置１Ａにおいて、ターボ圧縮機２自体の構成は第１実施形態（図１、図２参照）に示すものと同一であるため、各部に同一符号を付して説明は省略する。 [Third embodiment]
FIG. 4 is an overall view of a turbo refrigeration apparatus showing a third embodiment of the present invention. In this turbo refrigeration apparatus 1A, since the configuration of the turbo compressor 2 itself is the same as that shown in the first embodiment (see FIGS. 1 and 2), the same reference numerals are given to the respective components, and description thereof will be omitted.

このターボ冷凍装置１Ａにも、電源遮断時に主軸受１８ａ，１８ｂに代わってロータ軸１５を支持する補助軸受１９ａ，１９ｂの内部に冷媒Ｒを潤滑剤として供給する潤滑冷媒供給部４０が備えられている。この潤滑冷媒供給部４０は、液相状の冷媒Ｒが貯留された液冷媒貯留部４１と、この液冷媒貯留部４１と補助軸受１９ａ，１９ｂとの間を接続する液冷媒供給通路２７と、液冷媒供給通路２７に接続された電磁弁２８とを備えている。液冷媒供給通路２７は第１実施形態のものと同様に分岐通路２７ａ，２７ｂに分岐して補助軸受１９ａ，１９ｂに繋がっているが、液冷媒供給通路２７の上流側端部が凝縮器３ではなく液冷媒貯留部４１に接続されている点が異なっている。電磁弁２８は、第１実施形態のものと同じく通電された状態で閉となるノーマルオープン形式である。   This turbo refrigeration system 1A is also provided with a lubricating refrigerant supply unit 40 for supplying refrigerant R as a lubricant inside auxiliary bearings 19a and 19b supporting the rotor shaft 15 in place of the main bearings 18a and 18b when the power is turned off. I have. The lubricating refrigerant supply part 40 includes a liquid refrigerant storage part 41 storing the liquid refrigerant R, a liquid refrigerant supply passage 27 connecting the liquid refrigerant storage part 41 and the auxiliary bearings 19a, 19b, An electromagnetic valve 28 connected to the liquid refrigerant supply passage 27. The liquid refrigerant supply passage 27 is branched into branch passages 27a and 27b and connected to the auxiliary bearings 19a and 19b as in the first embodiment, but the upstream end of the liquid refrigerant supply passage 27 is connected to the condenser 3 in the condenser 3. And is connected to the liquid refrigerant storage section 41. The solenoid valve 28 is a normally open type that closes when energized in the same manner as in the first embodiment.

液冷媒貯留部４１としては、液相状の冷媒Ｒを、補助軸受１９ａ，１９ｂの周辺圧力よりも高い圧力を付与しながら貯留する圧力付与容器４３が用いられている。この圧力付与容器４３は、例えばシリンダ状の容器本体４４と、その中を軸方向に摺動自在に設けられたピストン４５と、このピストン４５を容器本体４４における液冷媒供給通路２７の接続された端面（ここでは下側の端面）の方に付勢するスプリング４６とを備えている。圧力付与容器４３（容器本体４４）の内部に貯留された液相状の冷媒Ｒは、ピストン４５を介してスプリング４６に押圧されることにより、補助軸受１９ａ，１９ｂの周辺圧力（ケーシング１３の内部圧力）よりも高い圧力を付与されている。   As the liquid refrigerant storage part 41, a pressure application container 43 that stores the liquid refrigerant R while applying a pressure higher than the peripheral pressure of the auxiliary bearings 19a and 19b is used. The pressure applying container 43 has, for example, a cylindrical container body 44, a piston 45 slidably provided in the container body 44 in the axial direction, and the piston 45 connected to the liquid refrigerant supply passage 27 in the container body 44. And a spring 46 biasing toward the end face (here, the lower end face). The liquid refrigerant R stored in the pressure applying container 43 (container main body 44) is pressed by the spring 46 via the piston 45, and thereby the peripheral pressure of the auxiliary bearings 19a and 19b (the internal pressure of the casing 13). Pressure).

以上のように構成されたターボ冷凍装置１Ａおよびターボ圧縮機２において、停電等により電源が遮断された場合には、非接触軸受である主軸受１８ａ，１８ｂの機能が停止し、これに代わって補助軸受１９ａ，１９ｂがロータ軸１５を支持する。これと同時に、通電された状態で閉となる電磁弁２８が、電源が遮断されたことによって開かれる。   In the turbo refrigeration apparatus 1A and the turbo compressor 2 configured as described above, when the power is cut off due to a power failure or the like, the functions of the main bearings 18a and 18b, which are non-contact bearings, stop, and instead, The auxiliary bearings 19a and 19b support the rotor shaft 15. At the same time, the solenoid valve 28 that closes when energized is opened when the power is cut off.

このため、液冷媒貯留部４１を構成する圧力付与容器４３の内部に貯留されてスプリング４６の付勢力によって補助軸受１９ａ，１９ｂの周辺圧力よりも高い圧力を付与された液相状の冷媒Ｒが、電磁弁２８の開弁と同時に圧力差によって液冷媒供給通路２７（分岐通路２７ａ，２７ｂ）を経て補助軸受１９ａ，１９ｂに供給される。このため、補助軸受１９ａ，１９ｂの内部に液相状の冷媒Ｒが潤滑剤として供給され、補助軸受１９ａ，１９ｂが潤滑、冷却される。   Therefore, the liquid-phase refrigerant R stored in the pressure applying container 43 constituting the liquid refrigerant storing section 41 and applied with a pressure higher than the peripheral pressure of the auxiliary bearings 19a and 19b by the urging force of the spring 46 is generated. At the same time as the opening of the solenoid valve 28, the pressure difference is supplied to the auxiliary bearings 19a and 19b via the liquid refrigerant supply passage 27 (branch passages 27a and 27b). Therefore, the liquid refrigerant R is supplied as a lubricant into the auxiliary bearings 19a and 19b, and the auxiliary bearings 19a and 19b are lubricated and cooled.

本構成によれば、ターボ圧縮機２により圧縮された冷媒を抽出する系統を設ける必要がないため、軸受システムを簡素化することができる。また、ターボ冷凍装置１Ａの運転状態によらず、潤滑用冷媒の供給圧力を必要規定値以上に保持することができ、潤滑用冷媒を確実に供給することができる。なお、圧力付与容器４３の構造は、必ずしも上記の構成でなくてもよく、例えばスプリング４６の付勢力に代えて錘の重量をピストン４５に加えるようにしてもよい。あるいは、圧力付与容器４３の内部をゴム膜で軸方向に２分割し、閉塞されている一方の部屋に窒素ガス等を封入し、冷媒供給通路２７が接続されている他方の部屋に冷媒Ｒを貯留するようにした、いわゆるアキュムレータ構造に変更してもよい。   According to this configuration, there is no need to provide a system for extracting the refrigerant compressed by the turbo compressor 2, and thus the bearing system can be simplified. Further, the supply pressure of the lubricating refrigerant can be maintained at a required value or more regardless of the operating state of the turbo refrigeration apparatus 1A, and the lubricating refrigerant can be reliably supplied. The structure of the pressure applying container 43 does not necessarily have to be the above-described structure. For example, the weight of the weight may be applied to the piston 45 instead of the urging force of the spring 46. Alternatively, the inside of the pressure applying container 43 is divided into two parts by a rubber film in the axial direction, nitrogen gas or the like is sealed in one closed room, and the refrigerant R is supplied to the other room to which the refrigerant supply passage 27 is connected. The storage may be changed to a so-called accumulator structure.

以上に説明したように、上記の各実施形態に係るターボ圧縮機２，２Ａおよびこれを備えたターボ冷凍装置１，１Ａによれば、ターボ圧縮機２，２Ａのロータ軸１５を支持する非接触軸受である主軸受１８ａ，１８ｂの機能停止時に、この主軸受１８ａ，１８ｂに隣接して設けられるタッチダウン用の補助軸受１９ａ，１９ｂに液冷媒を潤滑剤として供給可能にし、補助軸受１９ａ，１９ｂの低コスト化および長寿命化を図ることができる。   As described above, according to the turbo compressors 2 and 2A and the turbo refrigeration apparatuses 1 and 1A including the turbo compressors, the non-contact type supporting the rotor shaft 15 of the turbo compressors 2 and 2A is provided. When the main bearings 18a, 18b are stopped, the liquid refrigerant can be supplied as a lubricant to the touch-down auxiliary bearings 19a, 19b provided adjacent to the main bearings 18a, 18b. Can be reduced in cost and life can be prolonged.

なお、本発明は上記の各実施形態の構成のみに限定されるものではなく、適宜変更や改良を加えることができ、このように変更や改良を加えた実施形態も本発明の権利範囲に含まれるものとする。例えば、上記実施形態に記載したターボ冷凍装置１，１Ａの全体構成や用途、あるいはターボ圧縮機２，２Ａの構成等は、あくまでも一例であり、各部に変更を加えることもできる。   Note that the present invention is not limited to only the configuration of each of the above-described embodiments, and can be appropriately changed or improved. Embodiments with such changed or improved are also included in the scope of right of the present invention. Shall be For example, the overall configuration and use of the turbo refrigeration apparatuses 1 and 1A described in the above embodiment, or the configurations of the turbo compressors 2 and 2A are merely examples, and each part can be modified.

１，１Ａ ターボ冷凍装置
２，２Ａ ターボ圧縮機
３ 凝縮器
４ 蒸発器
７ 冷媒圧縮部
１３ ケーシング
１４ 電動機
１５ ロータ軸
１６ インペラ
１８ａ，１８ｂ 主軸受（非接触軸受）
１９ａ，１９ｂ 補助軸受
２５，３２，４０ 潤滑冷媒供給部
２６，３３，４１ 液冷媒貯留部
２７，３４ａ，３４ｂ 液冷媒供給通路
２８，３５ａ，３５ｂ 電磁弁
３１ 液冷媒ジャケット
４３ 圧力付与容器
Ｒ 冷媒 1, 1A turbo refrigeration system 2, 2A turbo compressor 3 condenser 4 evaporator 7 refrigerant compression unit 13 casing 14 motor 15 rotor shaft 16 impellers 18a, 18b main bearing (non-contact bearing)
19a, 19b Auxiliary bearings 25, 32, 40 Lubricating refrigerant supply units 26, 33, 41 Liquid refrigerant storage units 27, 34a, 34b Liquid refrigerant supply passages 28, 35a, 35b Solenoid valve 31 Liquid refrigerant jacket 43 Pressure applying container R Refrigerant

Claims (9)

ロータ軸と、
前記ロータ軸の中間部に同軸的に設けられて前記ロータ軸を回転駆動する電動機と、
前記ロータ軸の一端に固定されて冷媒を圧縮する冷媒圧縮部を構成するインペラと、
前記電動機と前記インペラとの間、および前記ロータ軸の他端を軸支する非接触軸受と、
前記非接触軸受に隣接し、該非接触軸受の機能停止時に該非接触軸受に代わって前記ロータ軸を軸支する補助軸受と、
前記非接触軸受の機能停止時に、前記補助軸受の内部に前記冷媒を潤滑剤として供給する潤滑冷媒供給部と、
を備えたターボ圧縮機。 A rotor shaft,
An electric motor that is provided coaxially with an intermediate portion of the rotor shaft and rotationally drives the rotor shaft;
An impeller fixed to one end of the rotor shaft and constituting a refrigerant compression unit that compresses refrigerant,
Non-contact bearing between the motor and the impeller, and supporting the other end of the rotor shaft,
An auxiliary bearing that is adjacent to the non-contact bearing and that supports the rotor shaft in place of the non-contact bearing when the non-contact bearing stops functioning;
When the function of the non-contact bearing is stopped, a lubricating refrigerant supply unit that supplies the refrigerant as a lubricant inside the auxiliary bearing,
Turbo compressor equipped with. 前記潤滑冷媒供給部は、
液相状の前記冷媒が貯留された液冷媒貯留部と、
前記補助軸受と前記液冷媒貯留部との間を接続する液冷媒供給通路と、
前記液冷媒供給通路に接続され、通電された状態で閉となる電磁弁と、
を備えて構成されている請求項１に記載のターボ圧縮機。 The lubricating refrigerant supply unit,
A liquid refrigerant storage unit in which the liquid refrigerant is stored,
A liquid refrigerant supply passage connecting between the auxiliary bearing and the liquid refrigerant storage section,
An electromagnetic valve connected to the liquid refrigerant supply passage and closed when energized,
The turbo compressor according to claim 1, further comprising: 前記液冷媒貯留部は、前記冷媒圧縮部により圧縮された前記冷媒が凝縮される凝縮器の底部である請求項２に記載のターボ圧縮機。   The turbo compressor according to claim 2, wherein the liquid refrigerant storage part is a bottom part of a condenser in which the refrigerant compressed by the refrigerant compression part is condensed. 前記液冷媒貯留部は、前記電動機を収容するケーシングに設けられた、前記電動機冷却用の液冷媒ジャケットである請求項２に記載のターボ圧縮機。   3. The turbo compressor according to claim 2, wherein the liquid refrigerant storage section is a liquid refrigerant jacket for cooling the motor, provided in a casing that houses the motor. 4. 前記液冷媒貯留部は、液相状の前記冷媒を、前記補助軸受の周辺圧力よりも高い圧力を付与しながら貯留する圧力付与容器である請求項２に記載のターボ圧縮機。   3. The turbo compressor according to claim 2, wherein the liquid refrigerant storage unit is a pressure application container that stores the liquid-phase refrigerant while applying a pressure higher than a peripheral pressure of the auxiliary bearing. 4. 前記補助軸受は転がり軸受であり、その外輪、内輪、および転動体の少なくともいずれかの材質としてセラミック材を採用した請求項１から５のいずれかに記載のターボ圧縮機。   The turbo compressor according to any one of claims 1 to 5, wherein the auxiliary bearing is a rolling bearing, and a ceramic material is employed as a material of at least one of an outer ring, an inner ring, and a rolling element. 前記補助軸受は転がり軸受であり、その外輪、内輪、および転動体の少なくともいずれかに、低粘度流体による潤滑でも潤滑膜が形成される材質をコーティングした請求項１から５のいずれかに記載のターボ圧縮機。   6. The auxiliary bearing according to claim 1, wherein at least one of an outer ring, an inner ring, and a rolling element is coated with a material capable of forming a lubricating film even when lubricated with a low-viscosity fluid. Turbo compressor. 前記補助軸受は転がり軸受であり、その外輪、内輪、および転動体の少なくともいずれかにダイヤモンドライクカーボンをコーティングした請求項１から５のいずれかに記載のターボ圧縮機。   The turbo compressor according to any one of claims 1 to 5, wherein the auxiliary bearing is a rolling bearing, and at least one of an outer ring, an inner ring, and a rolling element is coated with diamond-like carbon. 請求項１から８のいずれかに記載のターボ圧縮機と、
前記ターボ圧縮機によって圧縮された前記冷媒を凝縮させる凝縮器と、
凝縮した前記冷媒を蒸発させる蒸発器と、
を具備してなるターボ冷凍装置。 A turbo compressor according to any one of claims 1 to 8,
A condenser for condensing the refrigerant compressed by the turbo compressor,
An evaporator for evaporating the condensed refrigerant,
A turbo refrigeration apparatus comprising:
JP2016086202A 2016-04-22 2016-04-22 Turbo compressor, turbo refrigeration device provided with the same Active JP6672056B2 (en)

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JP2016086202A JP6672056B2 (en) 2016-04-22 2016-04-22 Turbo compressor, turbo refrigeration device provided with the same
US16/095,112 US20190211834A1 (en) 2016-04-22 2017-04-18 Turbo compressor and turbo refrigerator provided with same
CN201780038888.XA CN109416049A (en) 2016-04-22 2017-04-18 Turbo-compressor and the turbine refrigerating plant for having the turbo-compressor
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Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017143257A1 (en) * 2016-02-19 2017-08-24 Johnson Controls Technology Company Vapor compression system and method of extending service life of same
US10876539B2 (en) * 2016-09-07 2020-12-29 Hamilton Sunstrand Corporation Ventilation fan having a hybrid bearing system
WO2018207767A1 (en) * 2017-05-09 2018-11-15 ダイキン工業株式会社 Turbo compressor
WO2019171740A1 (en) * 2018-03-05 2019-09-12 パナソニック株式会社 Dynamic compressor and refrigeration cycle device
JP7187292B2 (en) * 2018-03-05 2022-12-12 パナソニックホールディングス株式会社 Speed compressor and refrigeration cycle equipment
JP2020128745A (en) * 2019-02-01 2020-08-27 ホワイト ナイト フルイド ハンドリング インコーポレーテッドＷｈｉｔｅ Ｋｎｉｇｈｔ Ｆｌｕｉｄ Ｈａｎｄｌｉｎｇ Ｉｎｃ． Pump having magnet for journaling and magnetically axially positioning rotor thereof, and related method
CN111828336A (en) * 2019-04-15 2020-10-27 孟想 Ultra-silent zero-leakage nuclear main pump/fan compressor integrated design scheme
EP3742080B1 (en) * 2019-05-21 2021-11-03 Carrier Corporation Refrigeration apparatus
EP3742069B1 (en) * 2019-05-21 2024-03-20 Carrier Corporation Refrigeration apparatus and use thereof
US11566663B2 (en) * 2019-06-26 2023-01-31 Trane International Inc. Bearing for supporting a rotating compressor shaft
JP2021055613A (en) * 2019-09-30 2021-04-08 ダイキン工業株式会社 Turbo compressor
WO2021067478A1 (en) * 2019-09-30 2021-04-08 Trane International Inc. Cooling of a compressor shaft gas bearing
GB2588146A (en) * 2019-10-09 2021-04-21 Edwards Ltd Vacuum pump
JP6927343B1 (en) * 2020-02-17 2021-08-25 ダイキン工業株式会社 Compressor
DE102020203204A1 (en) * 2020-03-12 2021-09-16 Robert Bosch Gesellschaft mit beschränkter Haftung Bearing arrangement for a shaft of a turbo compressor
US11846296B2 (en) * 2020-03-13 2023-12-19 Carrier Corporation Flushing of a touchdown bearing
JP2021161923A (en) * 2020-03-31 2021-10-11 ダイキン工業株式会社 Compressor
CN114198922B (en) * 2021-11-22 2023-08-15 青岛海尔空调电子有限公司 Liquid supply system of compressor
CN114483605B (en) * 2022-03-01 2023-11-21 江苏海拓宾未来工业科技集团有限公司 Two-stage impeller high-speed air suspension centrifugal blower turbine device
US20240077239A1 (en) * 2022-09-01 2024-03-07 Trane International Inc. Refrigerant circuit compressor gas bearing feed
JP2024057758A (en) * 2022-10-13 2024-04-25 三菱重工業株式会社 Cold energy power generation device and cold energy power generation system
CN116294299A (en) * 2023-01-04 2023-06-23 青岛海信日立空调***有限公司 Air conditioner for lubricating compressor bearing by refrigerant liquid

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0319498U (en) * 1989-07-07 1991-02-26
JPH10131889A (en) * 1996-10-25 1998-05-19 Mitsubishi Heavy Ind Ltd Compressor for perforator
US6176092B1 (en) * 1998-10-09 2001-01-23 American Standard Inc. Oil-free liquid chiller
JP2001123997A (en) * 1999-10-21 2001-05-08 Hitachi Ltd Centrifugal compressor with magnetic bearing
JP3866925B2 (en) * 2000-02-18 2007-01-10 株式会社日立産機システム Scroll compressor
US20060064197A1 (en) * 2005-01-26 2006-03-23 Denso Corporation Method and apparatus for designing rolling bearing to address brittle flaking
CN101326413B (en) * 2005-12-06 2012-04-25 开利公司 Lubrication system for acute stopping bearing of magnetic bearing compressor
DE102008031994B4 (en) * 2008-04-29 2011-07-07 Siemens Aktiengesellschaft, 80333 Fluid energy machine
EP2457076A1 (en) * 2009-07-22 2012-05-30 Johnson Controls Technology Company Apparatus and method for determining clearance of mechanical back-up bearings of turbomachinery utilizing electromagnetic bearings
EP2486296A4 (en) * 2009-10-09 2015-07-15 Dresser Rand Co Auxiliary bearing system with oil reservoir for magnetically supported rotor system
EP2677177B1 (en) * 2012-06-22 2020-10-14 Skf Magnetic Mechatronics Electric centrifugal compressor for vehicles
CN202711089U (en) * 2012-06-28 2013-01-30 河南中烟工业有限责任公司 Tobacco shred mixing and perfuming machine perfuming pipeline pressure stabilizing device
JP2014119083A (en) * 2012-12-19 2014-06-30 Daikin Ind Ltd Magnetic bearing device and compressor
DE102014212749A1 (en) * 2013-08-09 2015-02-12 Magna Powertrain Bad Homburg GmbH Method for operating a power-heat device, power heat device and use of a lubricant
JP6487163B2 (en) * 2014-07-31 2019-03-20 三菱重工サーマルシステムズ株式会社 Turbo refrigerator
CN205025807U (en) * 2015-10-14 2016-02-10 重庆美的通用制冷设备有限公司 Bearing assembly for centrifugal compressor

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