JP5714479B2 - Oil-cooled two-stage compressor and heat pump - Google Patents

Oil-cooled two-stage compressor and heat pump Download PDF

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JP5714479B2
JP5714479B2 JP2011284072A JP2011284072A JP5714479B2 JP 5714479 B2 JP5714479 B2 JP 5714479B2 JP 2011284072 A JP2011284072 A JP 2011284072A JP 2011284072 A JP2011284072 A JP 2011284072A JP 5714479 B2 JP5714479 B2 JP 5714479B2
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oil
pressure
flow path
space
stage
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JP2013133740A (en
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吉村　省二
省二 吉村
貴博 大上
貴博 大上
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Kobe Steel Ltd
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Priority to MYPI2012005174A priority patent/MY164694A/en
Priority to KR1020120150747A priority patent/KR101429363B1/en
Priority to CN201610562464.0A priority patent/CN106196674B/en
Priority to CN201210564832.7A priority patent/CN103175346B/en
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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
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/047—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of screw 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
    • 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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2519—On-off valves
    • 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
    • F25B2700/19—Pressures
    • 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
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1932—Oil pressures

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Description

本発明は、油冷式２段圧縮機及びヒートポンプに関する。   The present invention relates to an oil-cooled two-stage compressor and a heat pump.

油冷式圧縮機では、ロータ室内の空間であって、ロータによって吸込流路及び吐出流路から隔離された閉じ込み空間に、ロータの冷却、潤滑、シールのために、油が供給されるほか、軸封部や軸受部に油が供給される。そのため、圧縮機から吐出したガスに油が含まれるだけでなく、軸封部や軸受部からも油が流出する。軸封部等には所定量以上の油を供給することが必要であるため、例えば、特許文献１には、軸封部から流出した油を、当該油の圧力と略等しい圧力を有する圧縮機内の空間に環流させることが記載されている。具体的には、特許文献１に開示の油冷式圧縮機では、吐出側の軸封部から流出する油を、上記の閉じ込み空間に環流させている。   In oil-cooled compressors, oil is supplied to the confined space in the rotor chamber, which is separated from the suction flow path and the discharge flow path by the rotor, for cooling, lubrication, and sealing of the rotor. Oil is supplied to the shaft seal portion and the bearing portion. Therefore, not only oil is contained in the gas discharged from the compressor, but also the oil flows out from the shaft seal portion and the bearing portion. Since it is necessary to supply a predetermined amount or more of oil to the shaft seal portion or the like, for example, Patent Document 1 discloses that the oil flowing out from the shaft seal portion has a pressure approximately equal to the pressure of the oil. It is described that it is refluxed in the space. Specifically, in the oil-cooled compressor disclosed in Patent Document 1, oil flowing out from the shaft seal on the discharge side is circulated in the confined space.

しかしながら、圧縮機の用途によっては、吸込圧力と吐出圧力とが独立して変動する場合があり、吐出側の軸封部や軸受部から流出する油の圧力と等しい圧力となる部分を特定できるとは限らない。その場合、吐出側の軸封部や軸受部から流出する油は、吸込流路に環流されるように構成される。   However, depending on the application of the compressor, the suction pressure and the discharge pressure may fluctuate independently, and it is possible to identify a portion that has a pressure equal to the pressure of the oil flowing out from the shaft seal portion or the bearing portion on the discharge side. Is not limited. In that case, the oil flowing out from the shaft seal portion and the bearing portion on the discharge side is configured to circulate in the suction flow path.

圧縮機を用いて冷媒を循環させるヒートポンプ（冷凍機を含む）において、圧縮機の吸込圧力は蒸発器における冷媒の蒸発温度に依存し、圧縮機の吐出圧力は凝縮器における冷媒の凝縮温度に依存する。一般に、ヒートポンプに２段圧縮機を使用する場合、２段目の吐出側の軸封部や軸受部から流出した油は、中間圧力空間、つまり、１段目の圧縮機の吐出流路であって２段目の圧縮機の吸込流路に環流されるようになっている。   In heat pumps (including refrigerators) that circulate refrigerant using a compressor, the suction pressure of the compressor depends on the evaporation temperature of the refrigerant in the evaporator, and the discharge pressure of the compressor depends on the condensation temperature of the refrigerant in the condenser To do. In general, when a two-stage compressor is used in a heat pump, the oil flowing out from the shaft seal or bearing on the second-stage discharge side is in the intermediate pressure space, that is, the discharge passage of the first-stage compressor. Then, it is circulated through the suction flow path of the second stage compressor.

中間圧力空間の圧力（中間圧力）は、通常、ヒートポンプなどでは、吸込圧力と１段目の圧縮機の圧縮比とによって決定される。したがって、温熱源（又は冷却負荷）と冷熱源（または加熱負荷）の条件によっては、１段目の吸込圧力が上昇し、中間圧力が２段目の吐出圧力よりも高くなる場合がある。すると、従来の２段圧縮機では、２段目の吐出側の軸封部や軸受部を介した油の循環が滞り、軸受等が損傷するという問題が生じる。   The pressure (intermediate pressure) in the intermediate pressure space is usually determined by the suction pressure and the compression ratio of the first stage compressor in a heat pump or the like. Therefore, depending on the conditions of the heat source (or cooling load) and the cooling heat source (or heating load), the suction pressure in the first stage may increase, and the intermediate pressure may become higher than the discharge pressure in the second stage. Then, in the conventional two-stage compressor, there is a problem that the circulation of oil through the shaft seal portion and the bearing portion on the second-stage discharge side is stagnated and the bearings and the like are damaged.

２段目の吐出側の軸封部や軸受部から流出した油を１段目の吸込流路に環流させれば、油の循環を確保できるが、油の圧力と吸込圧力との差が大きい場合、吸込流路に供給された瞬間に油の圧力が低下し、油に溶け込んでいたガスが遊離（脱気）する。このガスの遊離は、歯溝圧力を上昇させて圧縮機の性能低下を招来する。一般に、ヒートポンプに使用する冷媒は、油に溶け込み易いため、冷媒の脱気による性能低下の問題が顕在化し易い。   If the oil flowing out from the shaft seal part or bearing part on the second-stage discharge side is circulated to the first-stage suction flow path, the oil circulation can be secured, but the difference between the oil pressure and the suction pressure is large. In this case, at the moment when the oil is supplied to the suction channel, the pressure of the oil decreases, and the gas dissolved in the oil is released (degassed). This liberation of gas raises the tooth gap pressure and causes a reduction in the performance of the compressor. In general, since the refrigerant used in the heat pump is easily dissolved in oil, the problem of performance deterioration due to the deaeration of the refrigerant is likely to become obvious.

実開平６−２２５８７号公報Japanese Utility Model Publication No. 6-22587

前記問題に鑑みて、本発明は、吸込圧力及び吐出圧力が変動しても油の循環を確保できるとともに性能が低下しない油冷式２段圧縮機及びヒートポンプを提供することを課題とする。   In view of the above problems, an object of the present invention is to provide an oil-cooled two-stage compressor and a heat pump that can ensure the circulation of oil even when the suction pressure and the discharge pressure fluctuate and the performance does not deteriorate.

前記課題を解決するために、本発明による油冷式２段圧縮機は、油分離器と、凝縮器と、膨脹弁と、蒸発器と共に介設されて、冷媒を封入した閉じた冷媒循環流路を構成する油冷式２段圧縮機であって、吸込流路から気体を吸い込んで油と共に圧縮し、中間圧力空間に吐出する第１段圧縮部と、前記中間圧力空間から気体を吸い込んで油と共に圧縮し、吐出流路に吐出する第２段圧縮部とからなり、前記第１段圧縮部のスクリュロータの一方と前記第２段圧縮部のスクリュロータの一方とが軸心を同じくして設けられ、前記第１段圧縮部の吸込流路、前記第１段圧縮部の吐出流路、前記中間圧力空間、前記第２段圧縮部の吸込流路、前記第２段圧縮部の吐出流路、及び軸受空間が、前記軸心に沿って順に設けられた油冷式２段圧縮機において、前記第２段圧縮部の吐出側の軸封構造及び軸受の少なくともいずれかに油を供給する油供給流路と、前記第２段圧縮部の吐出側の軸封構造及び軸受の少なくともいずれかから前記軸受空間に流出する油を前記第１段圧縮部の圧縮途中の空間である閉じ込み空間に環流させる油環流路とを有するものとする。
In order to solve the above-mentioned problems, an oil-cooled two-stage compressor according to the present invention includes an oil separator, a condenser, an expansion valve, an evaporator, and a closed refrigerant circulation flow that encloses a refrigerant. An oil-cooled two-stage compressor constituting a passage, which sucks a gas from a suction flow path and compresses it together with oil, and discharges the gas to an intermediate pressure space; and sucks a gas from the intermediate pressure space A second-stage compression section that compresses together with oil and discharges it to the discharge flow path, and one of the screw rotors of the first-stage compression section and one of the screw rotors of the second-stage compression section have the same axis. provided Te, suction passage of the first stage compression portion, the discharge flow path of said first stage compression portion, the intermediate pressure space, a suction flow path of the second-stage compression section, the discharge of the second stage compression section In the oil-cooled two-stage compressor in which the flow path and the bearing space are provided in order along the axis. From an oil supply channel for supplying oil to at least one of the shaft seal structure and the bearing on the discharge side of the second stage compression section, and at least one of the shaft seal structure and the bearing on the discharge side of the second stage compression section An oil ring flow path for circulating oil flowing out into the bearing space to a confined space that is a space in the middle of compression of the first stage compression portion is provided.

この構成によれば、吐出圧力の低下にともなって第２段圧縮部の吐出側の軸封構造や軸受から流出する油の圧力が低下しても、中間圧力空間よりもさらに圧力が低い閉じ込み空間に油を環流させるので、油の循環が確保でき、軸受の損傷等を防止できる。また、閉じ込み空間の圧力は吸込圧力よりも高いので、油の圧力に対する圧力差が大きくなりすぎず、吐出圧力が高いときに油に溶け込んだ気体が遊離することによって生じ得る性能低下を抑制できる。   According to this configuration, even if the pressure of the oil flowing out from the shaft seal structure or the bearing on the discharge side of the second-stage compression unit decreases as the discharge pressure decreases, the confinement is lower than the intermediate pressure space. Since oil is circulated through the space, oil circulation can be ensured and bearing damage can be prevented. In addition, since the pressure in the confined space is higher than the suction pressure, the pressure difference with respect to the oil pressure does not become too large, and the performance degradation that can be caused by the liberation of the gas dissolved in the oil when the discharge pressure is high can be suppressed. .

また、本発明の油冷式２段圧縮機において、前記油環流路は、分岐して前記中間圧力空間にも接続され、前記閉じ込み空間への流路を遮断可能な低圧開閉弁と、前記中間圧力空間への流路を遮断可能な高圧開閉弁とを備え、さらに、前記油供給流路の圧力が前記油環流路の圧力よりも高い場合には、前記低圧開閉弁を閉じて前記高圧開閉弁を開き、前記油供給流路の圧力が前記油環流路の圧力以下である場合には、前記低圧開閉弁を開いて前記高圧開閉弁を閉じる流路制御装置を有してもよい。   Further, in the oil-cooled two-stage compressor of the present invention, the oil ring flow path is branched and connected to the intermediate pressure space, and the low pressure on-off valve capable of blocking the flow path to the confined space; A high pressure on-off valve capable of shutting off a flow path to the intermediate pressure space, and further, when the pressure of the oil supply flow path is higher than the pressure of the oil ring flow path, the low pressure on-off valve is closed to A flow path control device may be provided that opens the on-off valve and closes the high-pressure on-off valve by opening the low-pressure on-off valve when the pressure of the oil supply passage is equal to or lower than the pressure of the oil ring passage.

この構成によれば、第２段圧縮部の吐出側の軸封構造や軸受から流出する油の圧力が高いときには、より高圧の中間圧力空間に油を環流させるので、油に溶け込んだ気体の遊離による性能低下をさらに抑制できる。また、流出する油の圧力が低いときには、閉じ込み空間に環流させることで、油の循環を確保できる。   According to this configuration, when the pressure of the oil flowing out from the shaft seal structure or the bearing on the discharge side of the second stage compression unit is high, the oil is circulated in the higher intermediate pressure space, so that the gas dissolved in the oil is released. The performance degradation due to can be further suppressed. Further, when the pressure of the oil flowing out is low, the circulation of the oil can be ensured by circulating in the confined space.

また、本発明によるヒートポンプは、前記油冷式２段圧縮機を有するものとする。   The heat pump according to the present invention includes the oil-cooled two-stage compressor.

また、Ｒ２４５ｆａを冷媒として冷水及び温水を製造するためのヒートポンプに本発明の油冷式２段圧縮機を適用する場合に予想される条件を勘案すると、前記閉じ込み空間は、圧力が前記吸込流路の圧力の１．１倍になる空間であることが好ましい。   In addition, considering the conditions expected when the oil-cooled two-stage compressor of the present invention is applied to a heat pump for producing cold water and hot water using R245fa as a refrigerant, the confined space has a pressure equal to the suction flow. A space that is 1.1 times the pressure of the passage is preferable.

本発明の第１実施形態のヒートポンプの構成図である。It is a lineblock diagram of the heat pump of a 1st embodiment of the present invention. 本発明の第２実施形態のヒートポンプの構成図である。It is a block diagram of the heat pump of 2nd Embodiment of this invention.

これより、本発明の実施形態について、図面を参照しながら説明する。先ず、図に、本発明の第１実施形態であるヒートポンプの構成を示す。本実施形態のヒートポンプ装置は、それ自体も本発明の１つの実施形態である油冷式２段スクリュ圧縮機１と、油分離器２と、凝縮器３と、膨張弁４と、蒸発器５とを介設してなり、冷媒（例えばＲ２４５ｆａ）を封入した閉じた冷媒循環流路６を構成する。   Embodiments of the present invention will now be described with reference to the drawings. First, the structure of the heat pump which is 1st Embodiment of this invention is shown in a figure. The heat pump apparatus according to the present embodiment itself is an oil-cooled two-stage screw compressor 1, an oil separator 2, a condenser 3, an expansion valve 4, and an evaporator 5 that are one embodiment of the present invention. And a closed refrigerant circulation channel 6 in which a refrigerant (for example, R245fa) is enclosed is formed.

油冷式２段スクリュ圧縮機１は、気体である冷媒を圧縮するが、このとき、冷却、潤滑及びシールのために、油を混合して冷媒を圧縮する。油冷式２段スクリュ圧縮機１が吐出した冷媒は、油分離器２に導入され、冷媒と油とが分離される。油分離器２において分離された油は、油冷式２段スクリュ圧縮機１の吐出圧によって、油冷式２段スクリュ圧縮機１に環流される。   The oil-cooled two-stage screw compressor 1 compresses a refrigerant that is a gas. At this time, the oil is mixed to compress the refrigerant for cooling, lubrication, and sealing. The refrigerant discharged from the oil-cooled two-stage screw compressor 1 is introduced into the oil separator 2, and the refrigerant and oil are separated. The oil separated in the oil separator 2 is circulated to the oil-cooled two-stage screw compressor 1 by the discharge pressure of the oil-cooled two-stage screw compressor 1.

油分離器２において油が除去された冷媒は、凝縮器３に導入される。凝縮器３は、冷媒と水との間で熱交換を行い、水を加熱して温水を製造する熱交換器である。凝縮器３において、冷媒は凝縮して液体になる。   The refrigerant from which oil has been removed in the oil separator 2 is introduced into the condenser 3. The condenser 3 is a heat exchanger that performs heat exchange between the refrigerant and water, and heats the water to produce hot water. In the condenser 3, the refrigerant is condensed into a liquid.

凝縮器３において凝縮した冷媒は、膨張弁４で減圧されて蒸発器５に供給される。蒸発器５は、冷媒と水との間で熱交換を行い、水を冷却して冷水を製造する熱交換器である。蒸発器５において、冷媒は蒸発して気体になる。蒸発器５において、蒸発した冷媒は、油冷式２段スクリュ圧縮機１に再供給される。   The refrigerant condensed in the condenser 3 is decompressed by the expansion valve 4 and supplied to the evaporator 5. The evaporator 5 is a heat exchanger that performs heat exchange between the refrigerant and water and cools the water to produce cold water. In the evaporator 5, the refrigerant evaporates into a gas. In the evaporator 5, the evaporated refrigerant is supplied again to the oil-cooled two-stage screw compressor 1.

油冷式２段スクリュ圧縮機１は、ハウジング７の中に第１段圧縮部８と第２段圧縮部９とが形成されている。   In the oil-cooled two-stage screw compressor 1, a first-stage compression section 8 and a second-stage compression section 9 are formed in a housing 7.

第１段圧縮部８は、ハウジング７に形成されたロータ室１０に雌雄一対のスクリュロータ１１を収容してなり、冷媒循環流路６に接続されるように形成された吸込流路１２から冷媒を吸い込んで圧縮し、吐出流路１３を介してハウジング７内に形成された中間圧力空間１４に吐出する。スクリュロータ１１は、ロータ室１０内の空間を区分して複数の閉鎖された閉じ込み空間１５を形成し、回転にともなって閉じ込み空間１５の容積を小さくすることにより、冷媒を圧縮する。このとき、第１段圧縮部８は、油とともに冷媒を吸い込んで、ハウジング７及びスクリュロータの冷却、並びに、スクリュロータ１１間及びスクリュロータ１１とロータ室１０の内壁との間のシール及び潤滑を行うようになっている。   The first stage compression section 8 accommodates a pair of male and female screw rotors 11 in a rotor chamber 10 formed in the housing 7, and the refrigerant from the suction flow path 12 formed so as to be connected to the refrigerant circulation flow path 6. Are sucked in and compressed, and discharged into the intermediate pressure space 14 formed in the housing 7 through the discharge flow path 13. The screw rotor 11 divides the space in the rotor chamber 10 to form a plurality of closed confining spaces 15, and compresses the refrigerant by reducing the volume of the confining space 15 as it rotates. At this time, the first stage compression unit 8 sucks the refrigerant together with the oil, cools the housing 7 and the screw rotor, and seals and lubricates between the screw rotors 11 and between the screw rotor 11 and the inner wall of the rotor chamber 10. To do.

また、第２段圧縮部９も、第１段圧縮部８と同様に、ハウジング７に形成されたロータ室１６に雌雄一対のスクリュロータ１７を収容してなり、吸込流路１８を介して中間圧力空間１４から冷媒を吸い込んで圧縮し、吐出流路１９を介して冷媒循環流路６に吐出する。第１段圧縮部８のスクリュロータ１１の一方と第２段圧縮部９のスクリュロータ１７の一方とは、その軸がモータ２０の出力軸と一体に接続されている。   Similarly to the first stage compression section 8, the second stage compression section 9 also includes a pair of male and female screw rotors 17 accommodated in a rotor chamber 16 formed in the housing 7, and is intermediate via a suction flow path 18. The refrigerant is sucked and compressed from the pressure space 14 and discharged to the refrigerant circulation passage 6 through the discharge passage 19. The shaft of one of the screw rotors 11 of the first-stage compression unit 8 and one of the screw rotors 17 of the second-stage compression unit 9 are integrally connected to the output shaft of the motor 20.

スクリュロータ１１，１７は、その軸が、軸受２１，２２，２３，２４によって支持されている。中間圧力空間１４は、第１段圧縮部８と第２段圧縮部９とを接続する冷媒の流路であるだけでなく、軸受２２，２３を収容する空間と一体であり、軸受２２，２３に潤滑のための油を供給するための流路でもある。同様に、第１段圧縮部８の吸込側及び第２段圧縮部９の吐出側には、軸受空間２５，２６が形成されている。軸受空間２５，２６は軸受２１，２４を潤滑するための油の流路にもなっている。   The shafts of the screw rotors 11 and 17 are supported by bearings 21, 22, 23 and 24. The intermediate pressure space 14 is not only a refrigerant flow path connecting the first-stage compression unit 8 and the second-stage compression unit 9, but is also integral with the space for housing the bearings 22, 23. It is also a flow path for supplying oil for lubrication. Similarly, bearing spaces 25 and 26 are formed on the suction side of the first stage compression unit 8 and the discharge side of the second stage compression unit 9. The bearing spaces 25 and 26 also serve as oil passages for lubricating the bearings 21 and 24.

第２段圧縮部９の吐出側の軸受２４には、潤滑のために、油分離器２から油供給流路２７を介して油が供給されるようになっている。軸受２４を潤滑した油は、軸受空間２６に流出する。油冷式２段スクリュ圧縮機１は、第２段圧縮部９の吐出側の軸受空間２６と、第１段圧縮部５の閉じ込み空間１５とを接続する油環流路２８を備える。尚、油環流路２８が閉じ込み空間１５と接続される位置での閉じ込み空間１５における冷媒の圧力は、吸込流路１２における冷媒の圧力の約１．１倍である。   Oil is supplied to the discharge-side bearing 24 of the second stage compression unit 9 from the oil separator 2 via the oil supply passage 27 for lubrication. The oil that has lubricated the bearing 24 flows out into the bearing space 26. The oil-cooled two-stage screw compressor 1 includes an oil ring passage 28 that connects the discharge-side bearing space 26 of the second-stage compression section 9 and the confining space 15 of the first-stage compression section 5. The refrigerant pressure in the confined space 15 at the position where the oil ring channel 28 is connected to the confined space 15 is approximately 1.1 times the refrigerant pressure in the suction channel 12.

軸受空間２６に流出する油の圧力は、油分離器２からの油の供給圧力、つまり、油冷式２段スクリュ圧縮機１（第２段圧縮部９）の吐出圧力と略同じで、軸受２４における圧力損失分だけ僅かに低い圧力になる。油冷式２段スクリュ圧縮機１の吐出圧力は、凝縮器３における凝縮温度によって決定される。本実施形態において想定される運転条件では、油冷式２段スクリュ圧縮機１の吐出圧力は、０．６１Ｍｐａまで低下する可能性がある。また、油冷式２段スクリュ圧縮機１（第１段圧縮部８）の吸込圧力は、蒸発器５における蒸発温度によって決定される。本実施形態においては、蒸発温度が最高６６℃となることを想定している。この場合、吸込圧力は、０．５４ＭＰａになる。したがって、油環流路２８が接続された第１段圧縮部５の閉じ込み空間１５の圧力は、吐出圧力の最低値である０．６１Ｍｐａと同じであり、油環流路２８を介した油の循環をぎりぎり確保できる。   The pressure of the oil flowing out into the bearing space 26 is substantially the same as the supply pressure of the oil from the oil separator 2, that is, the discharge pressure of the oil-cooled two-stage screw compressor 1 (second-stage compression section 9). The pressure is slightly lower by the pressure loss at 24. The discharge pressure of the oil-cooled two-stage screw compressor 1 is determined by the condensation temperature in the condenser 3. Under the operating conditions assumed in the present embodiment, the discharge pressure of the oil-cooled two-stage screw compressor 1 may be reduced to 0.61 Mpa. Further, the suction pressure of the oil-cooled two-stage screw compressor 1 (first stage compression unit 8) is determined by the evaporation temperature in the evaporator 5. In the present embodiment, it is assumed that the evaporation temperature is 66 ° C. at the maximum. In this case, the suction pressure is 0.54 MPa. Therefore, the pressure in the confined space 15 of the first stage compression unit 5 to which the oil ring passage 28 is connected is the same as 0.61 Mpa which is the lowest value of the discharge pressure, and the oil circulation through the oil ring passage 28 is performed. The last minute can be secured.

このように、本実施形態では、凝縮器３における凝縮温度が低く、蒸発器５における蒸発温度が高くなっても、油環流路２８を介して軸受空間２６から油を排出して、軸受２４への新たな油の供給を確保できる。また、閉じ込み空間１５は、吸込流路１２よりも圧力が高いため、油環流路２８を介して流入した油の圧力低下が少なくて済む。このため、油の圧力低下にともなって遊離する冷媒の量を少なくし、油冷式２段スクリュ圧縮機１の性能低下を抑制する。   As described above, in this embodiment, even when the condensation temperature in the condenser 3 is low and the evaporation temperature in the evaporator 5 is high, the oil is discharged from the bearing space 26 via the oil ring passage 28 to the bearing 24. The supply of new oil can be secured. Further, since the pressure in the confined space 15 is higher than that in the suction flow path 12, the pressure drop of the oil flowing in through the oil ring flow path 28 can be reduced. For this reason, the quantity of the refrigerant | coolant liberated with the pressure drop of oil is decreased, and the performance fall of the oil-cooled two-stage screw compressor 1 is suppressed.

続いて、図２に、本発明の第２実施形態のヒートポンプの構成を示す。尚、本実施形態において、第１実施形態と同じ構成要素には同じ符号を付して、重複する説明を省略する。本実施形態のヒートポンプでは、油環流路２８が分岐して、中間圧力空間１４にも接続されている。そして、油環流路２８は、閉じ込み空間１５への油の流路を遮断可能な低圧開閉弁２９と、中間圧力空間１４への油の流路を遮断可能な高圧開閉弁３０とを備えている。また、本実施形態の、油冷式２段スクリュ圧縮機１は、油分離器３から供給される油の圧力Ｐｄを検出する吐出圧力センサ３１と、中間圧力空間１４の圧力Ｐｍを検出する中間圧力センサ３２と、吐出圧力センサ３１及び中間圧力センサ３２の検出値に応じて低圧開閉弁２９及び高圧開閉弁３０を開閉する流路制御装置３３とを有する。   Then, in FIG. 2, the structure of the heat pump of 2nd Embodiment of this invention is shown. In the present embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and redundant description is omitted. In the heat pump of the present embodiment, the oil ring passage 28 is branched and connected to the intermediate pressure space 14. The oil ring flow path 28 includes a low pressure on-off valve 29 capable of blocking the oil flow path to the confined space 15 and a high pressure on-off valve 30 capable of blocking the oil flow path to the intermediate pressure space 14. Yes. Further, the oil-cooled two-stage screw compressor 1 of the present embodiment includes a discharge pressure sensor 31 that detects the pressure Pd of oil supplied from the oil separator 3 and an intermediate that detects the pressure Pm of the intermediate pressure space 14. A pressure sensor 32 and a flow path control device 33 that opens and closes the low-pressure on-off valve 29 and the high-pressure on-off valve 30 according to the detection values of the discharge pressure sensor 31 and the intermediate pressure sensor 32 are provided.

流路制御装置３３は、吐出圧力センサ３１が検出した圧力ｐｄと中間圧力センサ３２が検出した圧力Ｐｍとを比較し、吐出圧力センサ３１の検出した圧力ｐｄが中間圧力センサ３２の検出した圧力Ｐｍよりも高ければ、低圧開閉弁２９を閉鎖して高圧開閉弁３０を開放する一方、吐出圧力センサ３１の検出した圧力ｐｄが中間圧力センサ３２の検出した圧力Ｐｍ以下であれば、低圧開閉弁２９を開放して高圧開閉弁３０を閉鎖する。   The flow path control device 33 compares the pressure pd detected by the discharge pressure sensor 31 with the pressure Pm detected by the intermediate pressure sensor 32, and the pressure pd detected by the discharge pressure sensor 31 is the pressure Pm detected by the intermediate pressure sensor 32. If it is higher, the low pressure on-off valve 29 is closed and the high pressure on-off valve 30 is opened. On the other hand, if the pressure pd detected by the discharge pressure sensor 31 is less than or equal to the pressure Pm detected by the intermediate pressure sensor 32, Is opened to close the high-pressure on-off valve 30.

つまり、本実施形態は、吐出圧Ｐｄが高い場合には、第２段圧縮部９の吐出側の軸受空間２６に流出した油を、第１段圧縮部８の閉じ込み空間１５よりも圧力が高い中間圧力空間１４に環流させる。これにより、油の圧力低下にともなって油から遊離する冷媒の量を少なくし、油冷式２段スクリュ圧縮機１の吐出圧力が高いときの性能低下を小さくしている。また、本実施形態は、吐出圧Ｐｄが低い場合には、第２段圧縮部９の吐出側の軸受空間２６に流出した油を、第１実施形態と同様に、第１段圧縮部８の閉じ込み空間１５に環流させることで、油の循環を確保している。   That is, in the present embodiment, when the discharge pressure Pd is high, the oil flowing into the bearing space 26 on the discharge side of the second-stage compression unit 9 has a pressure higher than that of the confining space 15 of the first-stage compression unit 8. Reflux to the high intermediate pressure space 14. This reduces the amount of refrigerant liberated from the oil as the oil pressure drops, and reduces the performance drop when the discharge pressure of the oil-cooled two-stage screw compressor 1 is high. Further, in the present embodiment, when the discharge pressure Pd is low, the oil that has flowed into the bearing space 26 on the discharge side of the second-stage compression unit 9 is removed from the first-stage compression unit 8 as in the first embodiment. Circulating oil in the confined space 15 ensures oil circulation.

尚、上述の実施形態では、軸受２４から流出する油を油環流路２８を介して閉じ込み空間１５に環流させる例を説明したが、油供給流路２７から供給される油によって軸封を行う軸封構造を有する場合、第２段圧縮部９の吐出側の軸封構造から流出する油を油環流路２８を介して閉じ込み空間１５に環流させてもよい。   In the above-described embodiment, the example in which the oil flowing out from the bearing 24 is circulated to the confined space 15 via the oil ring flow path 28 has been described. However, the shaft is sealed with the oil supplied from the oil supply flow path 27. When the shaft seal structure is provided, the oil flowing out from the shaft seal structure on the discharge side of the second stage compression unit 9 may be circulated to the confined space 15 via the oil ring flow path 28.

１…油冷式２段スクリュ圧縮機
７…ハウジング
８…第１段圧縮部
９…第２段圧縮部
１０…ロータ室
１１…スクリュロータ
１２…吸込流路
１３…吐出流路
１４…中間圧力空間
１５…閉じ込み空間
１６…ロータ室
１７…スクリュロータ
１８…吸込流路
１９…吐出流路
２１，２２，２３，２４…軸受
２５，２６…軸受空間
２７…油供給流路
２８…油環流路
２９…低圧開閉弁
３０…高圧開閉弁
３１…吐出圧力センサ
３２…中間圧力センサ
３３…流路制御装置 DESCRIPTION OF SYMBOLS 1 ... Oil-cooled two-stage screw compressor 7 ... Housing 8 ... First stage compression part 9 ... Second stage compression part 10 ... Rotor chamber 11 ... Screw rotor 12 ... Suction passage 13 ... Discharge passage 14 ... Intermediate pressure space DESCRIPTION OF SYMBOLS 15 ... Confined space 16 ... Rotor chamber 17 ... Screw rotor 18 ... Suction flow path 19 ... Discharge flow path 21, 22, 23, 24 ... Bearing 25, 26 ... Bearing space 27 ... Oil supply flow path 28 ... Oil ring flow path 29 ... Low pressure on-off valve 30 ... High pressure on-off valve 31 ... Discharge pressure sensor 32 ... Intermediate pressure sensor 33 ... Flow path control device

Claims (4)

油分離器と、凝縮器と、膨脹弁と、蒸発器と共に介設されて、冷媒を封入した閉じた冷媒循環流路を構成する油冷式２段圧縮機であって、
吸込流路から気体を吸い込んで油と共に圧縮し、中間圧力空間に吐出する第１段圧縮部と、前記中間圧力空間から気体を吸い込んで油と共に圧縮し、吐出流路に吐出する第２段圧縮部とからなり、
前記第１段圧縮部のスクリュロータの一方と前記第２段圧縮部のスクリュロータの一方とが軸心を同じくして設けられ、
前記第１段圧縮部の吸込流路、前記第１段圧縮部の吐出流路、前記中間圧力空間、前記第２段圧縮部の吸込流路、前記第２段圧縮部の吐出流路、及び軸受空間が、前記軸心に沿って順に設けられた油冷式２段圧縮機において、
前記第２段圧縮部の吐出側の軸封構造及び軸受の少なくともいずれかに油を供給する油供給流路と、
前記第２段圧縮部の吐出側の軸封構造及び軸受の少なくともいずれかから前記軸受空間に流出する油を前記第１段圧縮部の圧縮途中の空間である閉じ込み空間に環流させる油環流路とを有することを特徴とする油冷式２段圧縮機。 An oil-cooled two-stage compressor that is provided together with an oil separator, a condenser, an expansion valve, and an evaporator to form a closed refrigerant circulation passage enclosing a refrigerant,
A first stage compression section that sucks gas from the suction flow path and compresses it with oil and discharges it to the intermediate pressure space; and a second stage compression that sucks gas from the intermediate pressure space and compresses it together with the oil and discharges it to the discharge flow path And consists of
One of the screw rotors of the first stage compression unit and one of the screw rotors of the second stage compression unit are provided with the same axis.
Suction passage of the first stage compression portion, the discharge flow path of said first stage compression portion, the intermediate pressure space, a suction flow path of the second-stage compression section, the discharge flow path of the second-stage compression section, and In the oil-cooled two-stage compressor in which the bearing space is provided in order along the axis,
An oil supply passage for supplying oil to at least one of a shaft seal structure and a bearing on the discharge side of the second-stage compression section;
An oil ring passage for circulating oil flowing out into the bearing space from at least one of a shaft seal structure and a bearing on the discharge side of the second stage compression section into a confined space that is a space in the middle of compression of the first stage compression section And an oil-cooled two-stage compressor. 前記油環流路は、分岐して前記中間圧力空間にも接続され、前記閉じ込み空間への流路を遮断可能な低圧開閉弁と、前記中間圧力空間への流路を遮断可能な高圧開閉弁とを備え、
さらに、前記油供給流路の圧力が前記油環流路の圧力よりも高い場合には、前記低圧開閉弁を閉じて前記高圧開閉弁を開き、前記油供給流路の圧力が前記油環流路の圧力以下である場合には、前記低圧開閉弁を開いて前記高圧開閉弁を閉じる流路制御装置を有することを特徴とする請求項１に記載の油冷式２段圧縮機。 The oil ring flow path is branched and connected to the intermediate pressure space, and a low pressure on-off valve capable of blocking the flow path to the confined space, and a high pressure on-off valve capable of blocking the flow path to the intermediate pressure space And
Further, when the pressure of the oil supply passage is higher than the pressure of the oil ring passage, the low pressure on-off valve is closed and the high pressure on-off valve is opened, and the pressure of the oil supply passage is The oil-cooled two-stage compressor according to claim 1, further comprising a flow path control device that opens the low-pressure on-off valve and closes the high-pressure on-off valve when the pressure is lower than the pressure. 前記閉じ込み空間は、圧力が前記吸込流路の圧力の１．１倍になる空間であることを特徴とする請求項１または２に記載の油冷式２段圧縮機。   3. The oil-cooled two-stage compressor according to claim 1, wherein the confined space is a space whose pressure is 1.1 times the pressure of the suction flow path. 請求項１から３のいずれかに記載の油冷式２段圧縮機を有するヒートポンプ。   A heat pump having the oil-cooled two-stage compressor according to any one of claims 1 to 3.
JP2011284072A 2011-12-26 2011-12-26 Oil-cooled two-stage compressor and heat pump Active JP5714479B2 (en)

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MYPI2012005174A MY164694A (en) 2011-12-26 2012-11-30 Oil-cooled two-stage compressor and heat pump
KR1020120150747A KR101429363B1 (en) 2011-12-26 2012-12-21 Oil-cooled two-stage compressor and heat pump
CN201610562464.0A CN106196674B (en) 2011-12-26 2012-12-24 Oil injection type split-compressor and heat pump
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