JP2004324507A - Horizontal rotary compressor - Google Patents

Horizontal rotary compressor Download PDF

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Publication number
JP2004324507A
JP2004324507A JP2003119469A JP2003119469A JP2004324507A JP 2004324507 A JP2004324507 A JP 2004324507A JP 2003119469 A JP2003119469 A JP 2003119469A JP 2003119469 A JP2003119469 A JP 2003119469A JP 2004324507 A JP2004324507 A JP 2004324507A
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JP
Japan
Prior art keywords
compression mechanism
oil supply
lubricating oil
motor
section
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JP2003119469A
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Japanese (ja)
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JP4223858B2 (en
Inventor
Masatsugu Konno
雅嗣 近野
Saho Funakoshi
砂穂 舟越
Hirokatsu Kosokabe
弘勝 香曽我部
Akihiko Ishiyama
明彦 石山
Kenichi Oshima
健一 大島
Yuugo Mukai
有吾 向井
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Hitachi Ltd
Hitachi Appliances Inc
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Hitachi Ltd
Hitachi Home and Life Solutions Inc
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Priority to JP2003119469A priority Critical patent/JP4223858B2/en
Priority to KR1020040007393A priority patent/KR100612811B1/en
Priority to CNA2004100082027A priority patent/CN1540166A/en
Publication of JP2004324507A publication Critical patent/JP2004324507A/en
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Publication of JP4223858B2 publication Critical patent/JP4223858B2/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3223—Cooling devices using compression characterised by the arrangement or type of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/0085—Prime movers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16N—LUBRICATING
    • F16N13/00—Lubricating-pumps
    • F16N13/20—Rotary pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16N—LUBRICATING
    • F16N7/00—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated
    • F16N7/38—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated with a separate pump; Central lubrication systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/98—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16N—LUBRICATING
    • F16N2210/00—Applications
    • F16N2210/16—Pumps

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

Abstract

<P>PROBLEM TO BE SOLVED: To surely supply a lubricating oil stored at a low side to a sliding part of a compressor mechanism part even when a compressor is largely inclined to any of a motor part side and the compressor mechanism part side. <P>SOLUTION: In this horizontal rotary compressor 40, the compressor mechanism part 42 for compressing a working fluid, and the motor part 41 connected to the compressor mechanism part 42 via a shaft 4 are stored in a sealed container 1 storing the lubricating oil at its bottom, and an oil supply means for supplying the lubricating oil to the sliding part of the compressor mechanism part 42 is provided. This oil supply means comprises: a first oil supply means for supplying the lubricating oil stored at the bottom part at the compressor mechanism part side to the sliding part of the compressor mechanism part 42; and a second oil supply means for supplying the lubricating oil at a bottom part at the motor part side to the sliding part of the compressor mechanism part 42. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

【０００１】
【発明の属する技術分野】
本発明は、横形ロータリ圧縮機に係り、特に自動車用空気調和機などに用いられる横形ロータリ圧縮機に好適なものである。
【０００２】
【従来の技術】
自動車用空気調和機の圧縮機には、高効率、高信頼性、低振動、低騒音などの基本性能はもちろん、省スペース、小形軽量、低コストであることが強く要求される。まとまった空間の少ないエンジンルームに圧縮機を載せるには、その省スペース性から横置きに設置できる圧縮機が望ましい。また、その圧縮機は小形軽量で安価なだけでなく、きびしい使用条件にさらされても高い信頼性を維持できなければならない。特に、自動車が坂道で長時間停車しているときや悪路を走行しているときなど、圧縮機が傾斜する状態においても問題なく運転できなければならない。
【０００３】
圧縮機の傾斜に対応できる横型密閉回転圧縮機として、例えば特開平１１−１８２４２９号公報（特許文献１）に開示されているものがある。この横型密閉回転圧縮機は、底部に潤滑油を貯留した密閉容器の内部に、モータと、その回転軸により駆動される回転圧縮機構と、回転軸の回転圧縮機構側の端部に設けられ、密閉容器底部に貯留された潤滑油に浸漬される給油管とを備え、給油管から吸い上げられた潤滑油を回転軸内部に設けられた給油路を通じて各摺動部に給油するように構成され、給油管の回転軸側基部付近に、横型密閉回転圧縮機の傾斜に応じて先端部が屈曲する可撓部を設けている。特許文献１には、この可撓部により圧縮機が傾斜しても給油管の先端部がそれに追従して給油を確保できるようにすることが記載されている。
【０００４】
【特許文献１】
特開平１１−１８２４２９号公報（図１）
【０００５】
【発明が解決しようとする課題】
従来の圧縮機では、モータ側（給油管を有する回転圧縮機構側と反対側）が低く傾斜した場合には、給油管が傾斜に追従するとしても給油管の先端部における潤滑油が少なくなって油面が下がってしまうので、確実な給油できなくなるという問題があった。さらには、モータ側が極端に低く傾斜した場合には、給油管の先端部に潤滑油自身が存在しない状態となって給油管の先端部が油面上方に露出し、給油が不可能になってしまうという問題があった。
【０００６】
本発明の目的は、圧縮機がモータ部側および圧縮機構部側の何れの側に大きく傾斜しても低い側に溜った潤滑油を圧縮機構部の摺動部に確実に供給することができ、高信頼性を確保できる横形ロータリ圧縮機を得ることにある。
【０００７】
なお、本発明のその他の目的と有利点は以下の記述から明らかにされる。
【０００８】
【課題を解決するための手段】
前記目的を達成するために、本発明は、底部に潤滑油を貯留した密閉容器内に、作動流体を圧縮する圧縮機構部と、この圧縮機構部にシャフトを介して接続したモータ部とを収納し、前記潤滑油を前記圧縮機構部の摺動部に供給する給油手段を備えた横形ロータリ圧縮機において、前記給油手段は、圧縮機構部側の底部の潤滑油を前記圧縮機構部の摺動部に供給する第１の給油手段と、前記モータ部側の底部の潤滑油を前記圧縮機構部の摺動部に供給する第２の給油手段とを有する構成としたものである。
本発明でさらに好ましくは、前記第１の給油手段は、前記圧縮機構部のシリンダ内を前記シャフトの回転に伴って偏心回転するローラに追随して往復動するベーンの下部に密閉的に形成されたベーンポンプ室と、前記密閉容器の底部の潤滑油を前記ベーンポンプ室へ吸入する吸入口と、前記ベーンポンプ室から前記圧縮機構部の摺動部に潤滑油を供給する給油路とを備えたベーンポンプを用いて構成することである。
また、前記圧縮機構部は第１および第２の圧縮部よりなる２組の圧縮部を備えて構成され、前記第１の圧縮部は、前記シャフトを軸支する主軸受、第１のシリンダ、仕切板、第１のローラおよび第１のベーンを備えて構成され、前記第２の圧縮部は、前記仕切板、第２のシリンダ、前記シャフトを軸支する副軸受、第２のローラおよび第２のベーンを備えて構成され、前記ベーンポンプは前記第２の圧縮部側に形成することである。
また、前記ベーンポンプ室への吸入口は、前記圧縮機構部を構成するシリンダおよび端板の当接面を含む少なくとも一方側に穿った凹溝により形成することである。
また、前記ベーンポンプ室から前記圧縮機構部の摺動部に潤滑油を供給する給油路の一部を、プレス加工により給油路を形作る溝を有する板で構成した給油用カバー２５を前記端板の側面側に固定することにより形成することである。
また、前記圧縮機構部を構成するモータ部側の端板により圧縮機構部側とモータ部側とを仕切り、前記端板の下部に圧縮機構部側とモータ部側とを連通する連通穴を設け、前記圧縮機構部の圧縮室の吐出口を前記モータ部側に連通するように設け、前記主軸受の上部に圧縮機構部側とモータ部側とを連通する絞り穴を設け、前記圧縮機構部側に圧縮機の外へ前記作動流体を吐出する吐出パイプを設けることである。
また、前記第２の給油手段は、前記密閉容器内を吐出圧とすると共に、一側端部が前記シャフトの貫通穴のモータ部側の開口に連通し且つ他側端部が前記密閉容器の底部に延びている給油用パイプを備えて構成することである。
また、前記給油用バイプを支持する支持部材に前記給油パイプを圧縮機全体の回転に伴って回転可能に取付けることである。
また、前記圧縮機構部の摺動部に連通する貫通穴を前記シャフトに設け、前記貫通穴の圧縮機構部側およびモータ部側の少なくとも一方の端部に遠心ポンプを設けることである。
【０００９】
【発明の実施の形態】
以下、本発明の横形ロータリ圧縮機の一実施例を、図１から図９を用いて説明する。
【００１０】
まず、本実施例の横形ロータリ圧縮機の全体構成に関して、図１および図２を参照しながら説明する。本実施例は横形２シリンダロータリ圧縮機の例である。
【００１１】
横形ロータリ圧縮機４０は、自動車用空気調和機の冷凍サイクルの構成要素として自動車のエンジンルームなどに配置されて使用される。この圧縮機４０は、密閉容器１内に、モータ部４１と、このモータ部４１により駆動される圧縮機構部４２とを収納して構成されている。
【００１２】
密閉容器１は、横長で円筒状の本体部と、その両側の蓋部とを備えて構成されている。モータ部４１は、密閉容器１に固定されたステータ２と、シャフト４を圧入したロータ３とを備えて構成されている。圧縮機構部４２は、シャフト４によりモータ部４１と直結しており、２組の圧縮部を備えて構成されている。
【００１３】
第１の圧縮部は、シャフト４を軸支する主軸受５、第１のシリンダ６、仕切板７、第１のローラ１２、第１のベーン１４、第１のスプリング１６により構成されている。第２の圧縮部は、仕切板７、第２のシリンダ８、シャフト４を軸支する副軸受９、第２のローラ１３、第２のベーン１５、第２のスプリング１７によって構成されている。前記二つのシリンダ６、８は、その中間に仕切板７を挟持し、その両側に主軸受５および副軸受９を配置することにより、これらで囲まれた二つの空間をシリンダ室として形成している。従って、主軸受５、仕切板７および副軸受９は、各シリンダ６、８に対する端板として機能する。そして、主軸受５は、密閉容器１に固定されており、密閉容器１内を圧縮機構部側とモータ部側とに仕切っている。
【００１４】
シャフト４は、その中央部を主軸受５に支持され、左右両側が圧縮機構部側およびモータ部側に延びており、中心部に左右に貫通する穴３３を設けている。この貫通穴３３は潤滑油を圧縮機構部４２の摺動部に供給するために形成されている。シャフト４の両端部は密閉容器１の両端部近くに位置しており、貫通穴３３が開口されている。シャフト４は互いに位相を１８０度異にする２個のクランク部１０、１１を有している。これらクランク部１０、１１にローラ１２、１３がそれぞれ自転自在に嵌合されている。このように、位相が１８０度異なる２組の圧縮部とすることにより圧縮部のバランスが良好になり低振動化を図ることができる。
【００１５】
次に、第１の圧縮部および第２の圧縮部の具体的構成および動作について図１および図２を参照しながら説明する。
【００１６】
シャフト４の回転に伴ってローラ１２、１３はシリンダ６、８内を偏心回転するようになっている。ベーン１４、１５は、密閉容器内のガス圧（吐出圧）とスプリング１６、１７によりローラ１２、１３に押圧され、シリンダ室内を吸入室１８と圧縮室１９に仕切っている。そして、ローラ１２、１３の偏心回転に追従して、シリンダ６、８のベーンスロット２０内で往復動する。
【００１７】
係る構成において、圧縮機４０の圧縮動作は以下のように行われる。モータ部４１に通電されると、ロータ３はシャフト４を駆動し、クランク部１１に嵌合されたローラ１２、１３がシリンダ６、８内を偏心回転する。これにより作動流体（例えば冷媒ガス）は、吸入パイプ２３より吸入口２１を通り、吸入室１８に吸入される。そして、吸入完了後、吸入室１８は圧縮室１９となり、圧縮室１９内で圧縮され、吐出弁（図示せず）を有する吐出口２２より吐出される。
【００１８】
第１の圧縮部では、作動流体はモータ部側へ吐出される。モータ部側へ吐出された作動流体は、主軸受５に設けた絞り穴３０を通って圧縮機構部側に至り、圧縮機構部側に開口した吐出パイプ２４より圧縮機外へ吐出される。第２の圧縮部では、作動流体は副軸受９と副軸受カバー２８により密閉された空間２８ａに吐出され、貫通穴２９を通ってモータ部側へ吐出される。このモータ部側へ吐出された作動流体は、第１の圧縮部から吐出された作動流体と混合して、主軸受５に設けた絞り穴３０を通って圧縮機構部側に至り、圧縮機構部側に開口した吐出パイプ２４より圧縮機外へ吐出される。ここで、潤滑油を含む作動流体は、絞り穴３０を通過した後、絞り穴３０に対向して圧縮機構側に設置された油分離用の板３７に衝突することで潤滑油を分離してから、吐出パイプ２４より圧縮機外へ吐出されるようになっている。分離された潤滑油は密閉容器１内の底部に集められる。
【００１９】
次に、圧縮機構部への給油手段について図１および図４を参照しながら説明する。
【００２０】
圧縮機構部４２の摺動部に潤滑油を供給する給油手段は、圧縮機構部側の底部の潤滑油を圧縮機構部４２の摺動部に供給する第１の給油手段と、モータ部側の底部の潤滑油を圧縮機構部４２の摺動部に供給する第２の給油手段とを有する。
【００２１】
第１の給油手段はベーンポンプを用いたものである。副軸受９に最も近いシリンダ８内を往復動するベーン１５の下部には、ベーン１５、シリンダ８、仕切板７、副軸受９によりベーンポンプ室１５ａが密閉的に形成され、これらによってベーンポンプが構成される。このベーンポンプを用いて、密閉容器１の底部に貯留した潤滑油を、給油路２６を通してシャフト４内の貫通穴３３へ圧送し、貫通穴３３に設けた横穴から軸受５、９の摺動部やローラ１２、１３の摺動部などへ給油する。なお、給油路２６は、副軸受９および副軸受カバー２８に設けられた貫通穴と、給油カバー１５の凹部により形成される空間とを連通することによって構成されており、ベーンポンプ室１５ａとシャフト４の貫通穴３３とを連通するものである。
【００２２】
第２の給油手段は密閉容器１内のモータ部側の圧力と圧縮機構部４２内の圧力との差圧を利用して給油するものである。シャフト４のモータ部側の端部には、給油用パイプ３４がシャフト４の貫通穴３３に連通されるように設けられている。給油用パイプ３４は、密閉容器１に固定された支持部材３５に一側端部が取付けられると共に、他側端部が密閉容器１内の底部に延びている。給油用パイプ３４の他側端部が位置する底部の潤滑油は、密閉容器内のモータ部側の吐出圧により、給油用パイプ３４を通してシャフト４内の貫通穴３３へ圧送され、貫通穴３３に設けた横穴から軸受５、９の摺動部やローラ１２、１３の摺動部などへ給油される。なお、支持部材３５はステータ２に固定されていてもよい。
【００２３】
次に、圧縮機４０が水平状態にあるときの第１の給油手段の給油動作について図３および図４を参照しながら説明する。
【００２４】
このベーンポンプは、図３にベーン１５が上死点の位置にあるときを示し、図４にベーン１５が下死点の位置にあるときを示す。ベーン１５が上方へ移動することにより、密閉容器１の底部に貯留した潤滑油は、吸入口２７からベーンポンプ室１５ａに吸入される。詳細に言えば、ベーン１５が上方へ移動する際には、給油路２６と吸入口２７の両者から吸入した潤滑油が図３に示すようにベーンポンプ室１５ａに吸入される。この吸入行程の前半においては、給油路２６内の潤滑油が有する慣性力のために、その逆流抵抗が大きいので、多くは吸入口２７から流入する。なお、この給油路２６内の慣性力は直前の吐出工程において給油路２６内の潤滑油が給油カバー側へ送られる状態から切換えられることにより発生する。
【００２５】
一方、ベーン１５が下方へ移動すると、ベーンポンプ室１５ａ内の潤滑油は押し出され、吐出行程となる。この吐出行程の前半では、給油路２６内の潤滑油の慣性力による流路抵抗に比べ、この流路と直交して設けた吸入口２７の抵抗の方が大きいので、吸入口２７から油溜り部へ逆流する油量は少なく、その多くは給油路２６側へ吐出される。
【００２６】
これらの動作を繰返すことで、吸入口２７から多少逆流する潤滑油以外は、給油路２６を通って摺動部へ供給されることになる。そして、圧縮機４０の水平状態における給油は、ベーンポンプにより行なわれるように設定されている。
【００２７】
また、ベーンポンプの吸入口２７はシリンダ８に穿った凹溝と副軸受９の外周部の縁とにより形成されている。これによって、テーパ形状の流体ダイオードを別に製作して給油路に挿入するものと比較して、低コスト、小形軽量の圧縮機４０とすることができる。
【００２８】
図５の変形例に示すように、シリンダ８に設ける凹溝による吸入穴２７の中心の位置を、ベーンスロット２０の中心から横にずらすようにすると、ベーン１５が下方に移動する際の下降流の影響を受けにくくなり、さらに給油効率が向上する。また、図６の変形例に示すように、ベーンポンプ室の吸入口２７を形成する穴を、シリンダ８の代わりに副軸受９に設けるようにしてもよい。
【００２９】
さらに本実施例では、圧縮機構部４２の摺動部へ確実に給油して高信頼性を確保するため、次のような構成としている。主軸受５により圧縮機構部４２とモータ部４１とは仕切られており、主軸受上部には絞り穴３０が設けられ、主軸受下部には潤滑油が圧縮機構部４２とモータ部４１を自由に移動できるように１つまたは複数の連通穴３１が設けられている。それぞれのシリンダ６、８から吐出された作動流体は一度モータ部側へ吐出され、主軸受上部に設けた絞り穴３０を通って圧縮機構部側へ移動する。絞り穴３０を通過する際、作動流体の圧力は低下するので、圧縮機構部側内の圧力はモータ部側より低くなる。この圧力差と釣り合うように、密閉容器１の底部に貯留した潤滑油は連通穴３１を通ってモータ部４１から圧縮機構部４２へ移動するので、圧縮機構部側の油面はモータ部側の油面より高くなる。そして、圧縮機構部側の油面をシャフト４に設けた給油用の貫通穴３３の位置より高くなるように設定することで、給油路２６を満たす潤滑油のヘッドが上がり、ベーンポンプの給油効率が向上することになる。また、モータ部側の油面をロータ３の下端より低くなるように設定することで、ロータ３の回転による潤滑油の攪拌を防ぐことができ、攪拌損失を低減できる。
【００３０】
圧縮機４０が傾斜したときの給油動作について図８および図９を参照しながら説明する。
【００３１】
図８は圧縮機構部側が相対的に下になるように圧縮機４０が傾斜した状態を示す図である。圧縮機構部側が下になるように傾斜すると、モータ部４１の底に溜った潤滑油は重力により連通穴３１を通って圧縮機構部側へ移動する。ベーンポンプの吸入口２７は密閉容器１の底に近い位置で且つ圧縮機構部側にあるので、吸入口２７の周辺には常に潤滑油が存在し、十分に潤滑油を摺動部へ供給することができる。ここで、潤滑油が直接吐出ポート２４を通って圧縮機外へ出ていかないようにするため、吐出ポート２４の開口部は潤滑油に浸らない位置、すなわち、圧縮機構部側の空間内で、できるだけ油面から遠くて、油分離板３７に対して作動流体が絞り穴３０を通った後衝突する側と逆側に近接した位置に設けている。
【００３２】
図９はモータ部側が相対的に下になるように圧縮機４０が傾斜した状態を示す図である。モータ部側が下になるように傾斜すると、圧縮機構部４２の底に溜った潤滑油は重力により連通穴３１を通ってモータ部側へ移動する。このとき、圧縮機構部側にほとんど潤滑油がない状態となるまで傾斜していると、ベーンポンプ内は作動流体（冷媒ガス）で満たされ、ベーンポンプは機能しなくなる。しかし、モータ部側に設けた給油用パイプ３４の吸入口は、モータ部４１の底に溜った潤滑油に浸っており、その吸入口周辺に十分な潤滑油が存在する状態となる。そして、モータ部側の圧力は圧縮機構部側の圧力より高いため、差圧によりモータ部側の潤滑油が給油用パイプ３４を通ってシャフト４の貫通穴３３に流入し、摺動部に供給されることになる。なお、圧縮機構部側とモータ部側との差圧により、作動流体も絞り穴３０、連通穴３１を通って圧縮機構部側に移動する。このとき、圧縮機構部４２とモータ部４１の圧力が等しくなり差圧給油が不可能とならないように、連通穴３１の穴径を設定している。
【００３３】
圧縮機４０が傾斜した場合、圧縮機構部側とモータ部側のどちらが下になるように傾斜しても、上述したように、常に潤滑油が十分に溜っている側から給油を行なうので、傾斜が大きくなっても確実に給油でき、高い信頼性を維持できる。
【００３４】
さらに本実施例では、摺動部へ確実に給油し高信頼性を確保するため、シャフト４の両端部に遠心ポンプ３２、３６を取付けている。遠心ポンプ３２、３６は平板の中央部に穴を開口した簡単な構造である。この遠心ポンプ３２、３６の作用を、圧縮機４０がほぼ水平かまたは圧縮機構部側が下になるように傾斜している場合、すなわち潤滑油の流れがベーンポンプから給油路２６を通って摺動部へ向かう場合について説明する。遠心ポンプ３２、３６は、シャフト４の貫通穴３３の入口を狭めるもので、ベーンポンプにより圧送されてきた潤滑油は遠心ポンプ３２の狭い入口を通ってシャフト４の貫通穴３３に入ろうとする。このとき、シャフト４は回転しているため潤滑油に遠心力が働き、入口を通過した後、シャフト４の径方向へ飛ばされて貫通穴３３の壁面まで移動する。この動作が連続することで、潤滑油を貫通穴３３内へ引き込もうとするポンプ作用が生じる。遠心ポンプ３６はシャフト４の貫通穴３３の出口部にあるので、潤滑油が遠心ポンプ３６を通過して貫通穴３３から出た後は、潤滑油に遠心力を発生させる力は働かず、ポンプ作用は生じない。この場合、遠心ポンプ３６は流路抵抗となり、シャフト４の貫通穴３３内に潤滑油を保持する役割を果たすので、摺動部へ十分に潤滑油を供給することができる。
【００３５】
圧縮機４０がモータ部側が下になるように傾斜しているとき、すなわち潤滑油の流れが給油用パイプ３４から摺動部へ向かう場合には、遠心ポンプ３２、３６はそれぞれ上記と逆の作用を行なう。この構成により、さらに確実に摺動部への給油ができ、信頼性が高められる。
【００３６】
なお、遠心ポンプ３２、３６の代わりに、公知の他の給油機構、例えば、シャフト４の内部に収容された、金属板をねじったパドルと称する給油機構や粘性ポンプなどでもよい。
【００３７】
さらに本実施例では、圧縮機４０がシャフト４の回転面で傾いたときにも摺動部へ確実に給油し高信頼性を確保するため、次のような構造としている。給油用パイプ３４は、シャフト４の回転面で回転自在になるように、支持部材３５に取付けられている。そして給油用パイプ３４の吸入口は、自重または付設したおもりにより、常に鉛直方向下向きに開口するようになっている。この構成により、圧縮機４０がシャフト４の回転面で傾いたときでも、給油用パイプ３４の吸入口は常に潤滑油に浸っており、摺動部へ確実に給油できる。なお、おもりを付設する場合には、磁石をおもりとして給油用パイプ３４の吸入口近傍に取付けることで、潤滑油中の摩耗粉などを吸着できるので、摺動部に摩耗粉などが侵入せず、高い信頼性を確保できる。
【００３８】
さらに本実施例では、低コストかつ小形軽量の圧縮機４０を提供するため、次のような構成としている。給油路２６の一部は副軸受カバー２８と給油用カバー２５により形成される。この給油用カバー２５を、図７に示すように、プレス加工により給油路を形作る溝を有する板で構成し、副軸受カバー２８とともに副軸受９に固定している。この構成により、ベーンポンプ室１５ａからシャフト４の貫通穴３３までをパイプで連結する必要がないので、パイプの曲げ加工や取付けの工程を省くことができ、低コストの圧縮機４０を提供できる。さらに、パイプを用いる場合には略コの字形に曲げる必要があるが、ある程度大きな半径で曲げなければならず、その分圧縮機４０の全長が長くなってしまうが、本実施例の構成にすることでこの問題を回避でき、小形軽量の圧縮機４０を提供することができる。
【００３９】
【発明の効果】
以上の実施例の説明から明らかなように、本発明によれば、圧縮機がモータ部側および圧縮機構部側の何れの側に大きく傾斜しても低い側に溜った潤滑油を圧縮機構部の摺動部に確実に供給することができ、高信頼性を確保できる横形ロータリ圧縮機が得られる。
【図面の簡単な説明】
【図１】本発明の一実施例に係る横形ロータリ圧縮機の縦断面図である。
【図２】図１のＡ−Ａ断面相当図である。
【図３】図１の横形ロータリ圧縮機のベーンが上死点の位置にあるときの要部拡大断面図である。
【図４】図１の横形ロータリ圧縮機のベーンが下死点の位置にあるときの要部拡大断面図である。
【図５】図１の横形ロータリ圧縮機の吸入口の変形例を示す図２相当図である。
【図６】図１の横形ロータリ圧縮機の吸入口の変形例を示す図１相当図である。
【図７】図１の横形ロータリ圧縮機に用いる給油用カバー単体の斜視図である。
【図８】図１の横形ロータリ圧縮機が圧縮機構部側に低く傾斜した状態の縦断面図である。
【図９】図１の横形ロータリ圧縮機が圧縮機構部側に低く傾斜した状態の縦断面図である。
【符号の説明】
１…密閉容器、２…ステータ、３…ロータ、４…シャフト、５…主軸受（端板）、６…第１のシリンダ、７…仕切板（端板）、８…第２のシリンダ、９…副軸受（端板）、１０、１１…クランク部、１２…第１のローラ、１３…第２のローラ、１４…第１のベーン、１５…第２のベーン、１６…第１のスプリング、１７…第２のスプリング、１８…吸入室、１９…圧縮室、２０…ベーンスロット、２４…吐出パイプ、２５…給油用カバー、２６…給油路、２７…ベーンポンプ吸入口、３０…絞り穴、３１…連通穴、３２、３６…遠心ポンプ、３４…給油用パイプ、３５…支持部材、４０…横形ロータリ圧縮機、４１…モータ部、４２…圧縮機構部。[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a horizontal rotary compressor, and is particularly suitable for a horizontal rotary compressor used for an air conditioner for an automobile or the like.
[0002]
[Prior art]
Compressors for air conditioners for automobiles are required to have not only basic performance such as high efficiency, high reliability, low vibration and low noise, but also space saving, small size and light weight, and low cost. In order to mount the compressor in an engine room with a small space, a compressor that can be installed horizontally is desirable because of its space saving. In addition, the compressor must be compact, lightweight and inexpensive, as well as maintain high reliability even when subjected to severe use conditions. In particular, the vehicle must be able to operate without problems even when the compressor is inclined, such as when the vehicle is stopped for a long time on a slope or running on a bad road.
[0003]
As a horizontal hermetic rotary compressor capable of coping with the inclination of the compressor, for example, there is one disclosed in Japanese Patent Application Laid-Open No. H11-182429 (Patent Document 1). This horizontal hermetic rotary compressor is provided inside a hermetic container storing lubricating oil at the bottom, a motor, a rotary compression mechanism driven by its rotary shaft, and an end of the rotary shaft on the rotary compression mechanism side, An oil supply pipe immersed in lubricating oil stored at the bottom of the sealed container, and configured to supply lubricating oil sucked up from the oil supply pipe to each sliding portion through an oil supply path provided inside the rotary shaft, A flexible portion is provided near the rotation shaft side base of the oil supply pipe, the tip of which is bent according to the inclination of the horizontal hermetic rotary compressor. Patent Literature 1 describes that even if the compressor is tilted by the flexible portion, the leading end of the oil supply pipe can follow the oil supply to secure oil supply.
[0004]
[Patent Document 1]
JP-A-11-182429 (FIG. 1)
[0005]
[Problems to be solved by the invention]
In the conventional compressor, when the motor side (the side opposite to the rotary compression mechanism side having the oil supply pipe) is inclined low, even if the oil supply pipe follows the inclination, the lubricating oil at the tip end of the oil supply pipe decreases. There was a problem that it was impossible to reliably refuel because the oil level was lowered. Further, when the motor side is extremely low inclined, the lubricating oil itself does not exist at the end of the oil supply pipe, and the end of the oil supply pipe is exposed above the oil level, so that lubrication becomes impossible. There was a problem that it would.
[0006]
An object of the present invention is to reliably supply lubricating oil accumulated on a lower side to a sliding portion of a compression mechanism section even if the compressor is greatly inclined to either a motor section side or a compression mechanism section side. Another object of the present invention is to obtain a horizontal rotary compressor that can ensure high reliability.
[0007]
Other objects and advantages of the present invention will be apparent from the following description.
[0008]
[Means for Solving the Problems]
In order to achieve the above-mentioned object, the present invention includes a compression mechanism for compressing a working fluid and a motor connected to the compression mechanism via a shaft in a closed container storing lubricating oil at a bottom portion. In a horizontal rotary compressor provided with oil supply means for supplying the lubricating oil to the sliding portion of the compression mechanism, the oil supply means slides the lubricating oil on the bottom of the compression mechanism toward the compression mechanism. And a second oil supply unit for supplying lubricating oil at the bottom of the motor unit side to a sliding portion of the compression mechanism unit.
More preferably, in the present invention, the first oil supply means is hermetically formed at a lower portion of a vane which reciprocates in a cylinder of the compression mechanism following a roller which rotates eccentrically with the rotation of the shaft. A vane pump having a vane pump chamber, a suction port for sucking lubricating oil at the bottom of the hermetic container into the vane pump chamber, and an oil supply passage for supplying lubricating oil from the vane pump chamber to a sliding portion of the compression mechanism. That is to say, it is configured.
Further, the compression mechanism section includes two sets of compression sections including a first and a second compression section, and the first compression section includes a main bearing that supports the shaft, a first cylinder, A partition plate, a first roller, and a first vane, wherein the second compression unit includes a partition plate, a second cylinder, a sub-bearing that supports the shaft, a second roller, and a second roller. 2 vanes, and the vane pump is formed on the second compression section side.
Further, the suction port to the vane pump chamber is formed by a concave groove formed on at least one side including a contact surface of a cylinder and an end plate constituting the compression mechanism.
Further, a part of an oil supply passage for supplying lubricating oil from the vane pump chamber to the sliding portion of the compression mechanism is formed by a plate having a groove having an oil supply passage formed by press working. It is formed by fixing to the side surface side.
Further, the compression mechanism section and the motor section side are separated by an end plate on the motor section side constituting the compression mechanism section, and a communication hole for communicating the compression mechanism section side and the motor section side is provided below the end plate. A discharge opening of a compression chamber of the compression mechanism section is provided so as to communicate with the motor section side, and a throttle hole communicating the compression mechanism section side and the motor section side is provided above the main bearing; A discharge pipe for discharging the working fluid to the outside of the compressor is provided on the side.
In addition, the second oil supply means sets the discharge pressure in the closed container, one end of which communicates with the opening of the through hole of the shaft on the motor portion side, and the other end of which is connected to the closed container. In other words, the fuel tank is provided with an oil supply pipe extending to the bottom.
Further, the oil supply pipe is rotatably attached to a support member supporting the oil supply pipe so as to rotate with the rotation of the entire compressor.
Further, a through-hole communicating with a sliding portion of the compression mechanism is provided in the shaft, and a centrifugal pump is provided at at least one end of the through-hole on the compression mechanism side and the motor side.
[0009]
BEST MODE FOR CARRYING OUT THE INVENTION
An embodiment of the horizontal rotary compressor according to the present invention will be described below with reference to FIGS.
[0010]
First, the overall configuration of the horizontal rotary compressor according to the present embodiment will be described with reference to FIGS. This embodiment is an example of a horizontal two-cylinder rotary compressor.
[0011]
The horizontal rotary compressor 40 is used as a component of a refrigeration cycle of an automotive air conditioner, for example, disposed in an engine room of an automobile. The compressor 40 is configured such that a motor unit 41 and a compression mechanism unit 42 driven by the motor unit 41 are housed in the sealed container 1.
[0012]
The closed container 1 includes a horizontally long, cylindrical main body, and lids on both sides thereof. The motor unit 41 includes the stator 2 fixed to the closed casing 1 and the rotor 3 into which the shaft 4 is press-fitted. The compression mechanism section 42 is directly connected to the motor section 41 by the shaft 4, and includes two sets of compression sections.
[0013]
The first compression unit includes a main bearing 5 that supports the shaft 4, a first cylinder 6, a partition plate 7, a first roller 12, a first vane 14, and a first spring 16. The second compression section includes a partition plate 7, a second cylinder 8, an auxiliary bearing 9 that supports the shaft 4, a second roller 13, a second vane 15, and a second spring 17. The two cylinders 6 and 8 sandwich the partition plate 7 in the middle and arrange the main bearing 5 and the sub-bearing 9 on both sides thereof to form two spaces surrounded by these as a cylinder chamber. I have. Therefore, the main bearing 5, the partition plate 7, and the auxiliary bearing 9 function as end plates for the respective cylinders 6, 8. The main bearing 5 is fixed to the closed casing 1 and partitions the inside of the closed casing 1 into a compression mechanism side and a motor side.
[0014]
The shaft 4 has a central portion supported by the main bearing 5, left and right sides extending to the compression mechanism portion side and the motor portion side, and a hole 33 penetrating left and right at the center portion. The through hole 33 is formed to supply lubricating oil to the sliding portion of the compression mechanism 42. Both ends of the shaft 4 are located near both ends of the closed container 1, and a through hole 33 is opened. The shaft 4 has two crank portions 10 and 11 whose phases are different from each other by 180 degrees. Rollers 12 and 13 are fitted to these crank portions 10 and 11 so that they can rotate freely. As described above, by using two sets of the compression units having phases different from each other by 180 degrees, the balance of the compression units is improved, and the vibration can be reduced.
[0015]
Next, specific configurations and operations of the first compression unit and the second compression unit will be described with reference to FIGS. 1 and 2.
[0016]
As the shaft 4 rotates, the rollers 12 and 13 rotate eccentrically in the cylinders 6 and 8. The vanes 14 and 15 are pressed by rollers 12 and 13 by gas pressure (discharge pressure) in a closed container and springs 16 and 17 to partition a cylinder chamber into a suction chamber 18 and a compression chamber 19. Then, following the eccentric rotation of the rollers 12 and 13, they reciprocate in the vane slots 20 of the cylinders 6 and 8.
[0017]
In such a configuration, the compression operation of the compressor 40 is performed as follows. When the motor unit 41 is energized, the rotor 3 drives the shaft 4, and the rollers 12 and 13 fitted to the crank unit 11 rotate eccentrically in the cylinders 6 and 8. As a result, the working fluid (for example, refrigerant gas) is sucked into the suction chamber 18 from the suction pipe 23 through the suction port 21. After the suction is completed, the suction chamber 18 becomes a compression chamber 19, is compressed in the compression chamber 19, and is discharged from a discharge port 22 having a discharge valve (not shown).
[0018]
In the first compression section, the working fluid is discharged to the motor section side. The working fluid discharged to the motor portion passes through the throttle hole 30 provided in the main bearing 5 to reach the compression mechanism portion side, and is discharged out of the compressor through a discharge pipe 24 opened to the compression mechanism portion side. In the second compression section, the working fluid is discharged into a space 28a sealed by the sub-bearing 9 and the sub-bearing cover 28, and is discharged through the through hole 29 to the motor section side. The working fluid discharged to the motor section side is mixed with the working fluid discharged from the first compression section, reaches the compression mechanism section side through the throttle hole 30 provided in the main bearing 5, and is compressed. It is discharged out of the compressor from a discharge pipe 24 opened to the side. Here, the working fluid containing the lubricating oil passes through the throttle hole 30 and then collides with an oil separating plate 37 provided on the compression mechanism side opposite to the throttle hole 30 to separate the lubricating oil. From the discharge pipe 24 to the outside of the compressor. The separated lubricating oil is collected at the bottom in the closed container 1.
[0019]
Next, oil supply means for the compression mechanism will be described with reference to FIGS.
[0020]
The lubricating means for supplying the lubricating oil to the sliding portion of the compression mechanism section 42 includes first lubricating means for supplying the lubricating oil on the bottom of the compression mechanism section to the sliding section of the compression mechanism section 42, Second lubrication means for supplying the lubricating oil at the bottom to the sliding portion of the compression mechanism section.
[0021]
The first oil supply means uses a vane pump. A vane pump chamber 15a is hermetically formed below the vane 15 reciprocating in the cylinder 8 closest to the sub-bearing 9 by the vane 15, the cylinder 8, the partition plate 7, and the sub-bearing 9, and these constitute a vane pump. You. Using this vane pump, the lubricating oil stored in the bottom of the sealed container 1 is pressure-fed to the through hole 33 in the shaft 4 through the oil supply passage 26, and the sliding portions of the bearings 5, 9 and Oil is supplied to the sliding portions of the rollers 12 and 13. The oil supply passage 26 is formed by communicating a through hole provided in the auxiliary bearing 9 and the auxiliary bearing cover 28 with a space formed by a concave portion of the oil supply cover 15, and the vane pump chamber 15 a is connected to the shaft 4. And the through hole 33.
[0022]
The second refueling means refuels using a pressure difference between the pressure in the motor unit side in the sealed container 1 and the pressure in the compression mechanism unit 42. An oil supply pipe 34 is provided at an end of the shaft 4 on the motor section side so as to communicate with the through hole 33 of the shaft 4. One end of the oil supply pipe 34 is attached to a support member 35 fixed to the closed container 1, and the other end extends to the bottom in the closed container 1. The lubricating oil at the bottom where the other end of the refueling pipe 34 is located is pressure-fed to the through hole 33 in the shaft 4 through the refueling pipe 34 by the discharge pressure of the motor unit side in the closed container. Oil is supplied to the sliding portions of the bearings 5 and 9 and the sliding portions of the rollers 12 and 13 from the lateral holes provided. Note that the support member 35 may be fixed to the stator 2.
[0023]
Next, the refueling operation of the first refueling means when the compressor 40 is in the horizontal state will be described with reference to FIGS.
[0024]
The vane pump is shown in FIG. 3 when the vane 15 is located at the top dead center, and in FIG. 4 when the vane 15 is located at the bottom dead center. As the vane 15 moves upward, the lubricating oil stored at the bottom of the closed container 1 is sucked into the vane pump chamber 15a from the suction port 27. More specifically, when the vane 15 moves upward, lubricating oil sucked from both the oil supply passage 26 and the suction port 27 is sucked into the vane pump chamber 15a as shown in FIG. In the first half of the suction stroke, the backflow resistance is large due to the inertial force of the lubricating oil in the oil supply passage 26, so that most of the oil flows from the suction port 27. The inertial force in the oil supply passage 26 is generated by switching from a state in which the lubricating oil in the oil supply passage 26 is sent to the oil supply cover side in the immediately preceding discharge step.
[0025]
On the other hand, when the vane 15 moves downward, the lubricating oil in the vane pump chamber 15a is pushed out, and the discharge stroke starts. In the first half of the discharge stroke, the resistance of the suction port 27 provided orthogonal to the flow path is larger than the resistance of the flow path due to the inertia force of the lubricating oil in the oil supply path 26. The amount of oil flowing back to the section is small, and most of the oil is discharged to the oil supply passage 26 side.
[0026]
By repeating these operations, lubricating oil other than the lubricating oil flowing somewhat backward from the suction port 27 is supplied to the sliding portion through the oil supply passage 26. The oil supply in the horizontal state of the compressor 40 is set to be performed by the vane pump.
[0027]
Further, the suction port 27 of the vane pump is formed by a concave groove formed in the cylinder 8 and an outer peripheral edge of the auxiliary bearing 9. As a result, the compressor 40 can be made lower in cost, smaller in size and lighter than the one in which a tapered fluid diode is separately manufactured and inserted into the oil supply passage.
[0028]
As shown in the modification of FIG. 5, when the position of the center of the suction hole 27 formed by the concave groove provided in the cylinder 8 is shifted laterally from the center of the vane slot 20, the downward flow when the vane 15 moves downward And the refueling efficiency is further improved. Further, as shown in a modified example of FIG. 6, a hole forming the suction port 27 of the vane pump chamber may be provided in the sub bearing 9 instead of the cylinder 8.
[0029]
Further, in the present embodiment, the following configuration is adopted in order to reliably lubricate the sliding portion of the compression mechanism section 42 and secure high reliability. The compression mechanism section 42 and the motor section 41 are partitioned by the main bearing 5, the throttle hole 30 is provided in the upper section of the main bearing, and the lubricating oil freely flows through the compression mechanism section 42 and the motor section 41 in the lower section of the main bearing. One or more communication holes 31 are provided so as to be movable. The working fluid discharged from each of the cylinders 6 and 8 is discharged once to the motor unit side, and moves to the compression mechanism unit side through the throttle hole 30 provided in the upper part of the main bearing. When passing through the throttle hole 30, the pressure of the working fluid decreases, so that the pressure in the compression mechanism side is lower than that in the motor section side. The lubricating oil stored at the bottom of the sealed container 1 moves from the motor 41 to the compression mechanism 42 through the communication hole 31 so as to balance this pressure difference. It is higher than the oil level. By setting the oil level on the compression mechanism side higher than the position of the oil supply through hole 33 provided in the shaft 4, the head of the lubricating oil filling the oil supply passage 26 rises, and the oil supply efficiency of the vane pump increases. Will be improved. Further, by setting the oil level on the motor section side to be lower than the lower end of the rotor 3, it is possible to prevent the lubricating oil from being agitated by the rotation of the rotor 3, and to reduce the agitation loss.
[0030]
The refueling operation when the compressor 40 is tilted will be described with reference to FIGS.
[0031]
FIG. 8 is a view showing a state where the compressor 40 is inclined such that the compression mechanism side is relatively lower. When the compression mechanism side is inclined downward, the lubricating oil collected at the bottom of the motor section 41 moves to the compression mechanism side through the communication hole 31 by gravity. Since the suction port 27 of the vane pump is located near the bottom of the closed casing 1 and on the side of the compression mechanism, lubricating oil is always present around the suction port 27, and the lubricating oil must be sufficiently supplied to the sliding portion. Can be. Here, in order to prevent the lubricating oil from directly going out of the compressor through the discharge port 24, the opening of the discharge port 24 is located at a position not immersed in the lubricating oil, that is, in the space on the compression mechanism side. It is provided at a position as far as possible from the oil level and close to the side opposite to the side where the working fluid collides with the oil separating plate 37 after passing through the throttle hole 30.
[0032]
FIG. 9 is a diagram showing a state where the compressor 40 is inclined such that the motor section side is relatively lower. When the motor section is inclined downward, the lubricating oil collected at the bottom of the compression mechanism section 42 moves to the motor section side through the communication hole 31 by gravity. At this time, if the compressor mechanism is inclined until there is almost no lubricating oil on the side of the compression mechanism, the inside of the vane pump is filled with the working fluid (refrigerant gas), and the vane pump stops functioning. However, the suction port of the oil supply pipe 34 provided on the motor section side is immersed in the lubricating oil accumulated at the bottom of the motor section 41, and there is a state where sufficient lubricating oil exists around the suction port. Since the pressure on the motor part side is higher than the pressure on the compression mechanism part side, the lubricating oil on the motor part side flows into the through hole 33 of the shaft 4 through the oil supply pipe 34 due to the differential pressure and is supplied to the sliding part. Will be done. The working fluid also moves toward the compression mechanism through the throttle hole 30 and the communication hole 31 due to the pressure difference between the compression mechanism and the motor. At this time, the hole diameter of the communication hole 31 is set so that the pressures of the compression mechanism 42 and the motor 41 are not equal to each other and the differential pressure lubrication becomes impossible.
[0033]
When the compressor 40 is tilted, the lubrication oil is always supplied from the side where the lubricating oil is sufficiently accumulated as described above, regardless of which of the compression mechanism portion and the motor portion is tilted downward. Even if the size becomes large, lubrication can be ensured and high reliability can be maintained.
[0034]
Further, in this embodiment, centrifugal pumps 32 and 36 are attached to both ends of the shaft 4 in order to reliably supply oil to the sliding portion and to ensure high reliability. The centrifugal pumps 32 and 36 have a simple structure in which a hole is opened at the center of the flat plate. The operation of the centrifugal pumps 32 and 36 is performed when the compressor 40 is substantially horizontal or inclined so that the compression mechanism side is downward, that is, the flow of the lubricating oil flows from the vane pump through the oil supply passage 26 to the sliding portion. The case of going to will be described. The centrifugal pumps 32 and 36 narrow the entrance of the through hole 33 of the shaft 4, and the lubricating oil pumped by the vane pump tries to enter the through hole 33 of the shaft 4 through the narrow entrance of the centrifugal pump 32. At this time, since the shaft 4 is rotating, centrifugal force acts on the lubricating oil, and after passing through the inlet, the lubricating oil is blown in the radial direction of the shaft 4 and moves to the wall surface of the through hole 33. When this operation is continued, a pump action for drawing the lubricating oil into the through hole 33 occurs. Since the centrifugal pump 36 is located at the outlet of the through hole 33 of the shaft 4, after the lubricating oil passes through the centrifugal pump 36 and exits from the through hole 33, the centrifugal force is not exerted on the lubricating oil. No effect occurs. In this case, the centrifugal pump 36 serves as a flow path resistance and plays a role of retaining the lubricating oil in the through hole 33 of the shaft 4, so that the lubricating oil can be sufficiently supplied to the sliding portion.
[0035]
When the compressor 40 is inclined so that the motor section side is downward, that is, when the flow of the lubricating oil is directed from the oil supply pipe 34 to the sliding section, the centrifugal pumps 32 and 36 operate in the opposite manner to the above. Perform With this configuration, oil can be more reliably supplied to the sliding portion, and reliability is improved.
[0036]
Instead of the centrifugal pumps 32 and 36, another known oil supply mechanism, for example, an oil supply mechanism called a paddle with a twisted metal plate housed inside the shaft 4 or a viscous pump may be used.
[0037]
Further, in the present embodiment, the following structure is adopted in order to surely supply oil to the sliding portion even when the compressor 40 is inclined on the rotation surface of the shaft 4 and to secure high reliability. The oil supply pipe 34 is attached to the support member 35 so as to be rotatable on the rotation surface of the shaft 4. The inlet of the refueling pipe 34 is always opened vertically downward by its own weight or an attached weight. With this configuration, even when the compressor 40 is tilted on the rotation surface of the shaft 4, the suction port of the oil supply pipe 34 is always immersed in the lubricating oil, and the sliding portion can be reliably supplied with oil. In the case where a weight is attached, by attaching a magnet as a weight near the suction port of the oil supply pipe 34, wear powder and the like in the lubricating oil can be absorbed, so that the wear powder and the like do not enter the sliding portion. , High reliability can be secured.
[0038]
Further, in the present embodiment, the following configuration is provided in order to provide a low-cost, compact and lightweight compressor 40. A part of the oil supply passage 26 is formed by the auxiliary bearing cover 28 and the oil supply cover 25. As shown in FIG. 7, the oil supply cover 25 is formed of a plate having a groove for forming an oil supply passage by press working, and is fixed to the auxiliary bearing 9 together with the auxiliary bearing cover 28. With this configuration, there is no need to connect the vane pump chamber 15a to the through hole 33 of the shaft 4 with a pipe, so that the pipe bending and mounting steps can be omitted, and the low-cost compressor 40 can be provided. Furthermore, when a pipe is used, it is necessary to bend in a substantially U-shape, but it must be bent with a large radius to some extent, and the overall length of the compressor 40 becomes longer by that amount. Thus, this problem can be avoided, and the compact and lightweight compressor 40 can be provided.
[0039]
【The invention's effect】
As apparent from the above description of the embodiment, according to the present invention, even if the compressor is greatly inclined to either the motor section side or the compression mechanism section side, the lubricating oil accumulated on the lower side is compressed by the compression mechanism section. The horizontal rotary compressor can be reliably supplied to the sliding portion of the rotary compressor and high reliability can be obtained.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a horizontal rotary compressor according to one embodiment of the present invention.
FIG. 2 is a cross-sectional view corresponding to the line AA in FIG.
3 is an enlarged sectional view of a main part of the horizontal rotary compressor of FIG. 1 when a vane is at a position of a top dead center.
4 is an enlarged sectional view of a main part of the horizontal rotary compressor of FIG. 1 when a vane is located at a bottom dead center.
5 is a diagram corresponding to FIG. 2, showing a modified example of the suction port of the horizontal rotary compressor of FIG. 1;
FIG. 6 is a diagram corresponding to FIG. 1, showing a modification of the suction port of the horizontal rotary compressor of FIG. 1;
FIG. 7 is a perspective view of a single lubrication cover used in the horizontal rotary compressor of FIG. 1;
8 is a longitudinal sectional view of the horizontal rotary compressor of FIG. 1 in a state where the horizontal rotary compressor is inclined low toward the compression mechanism.
9 is a longitudinal sectional view of the horizontal rotary compressor of FIG. 1 in a state where the horizontal rotary compressor is inclined low toward the compression mechanism.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Closed container, 2 ... Stator, 3 ... Rotor, 4 ... Shaft, 5 ... Main bearing (end plate), 6 ... 1st cylinder, 7 ... Partition plate (end plate), 8 ... 2nd cylinder, 9 ... sub bearings (end plates), 10, 11 ... crank parts, 12 ... first rollers, 13 ... second rollers, 14 ... first vanes, 15 ... second vanes, 16 ... first springs, 17 second spring, 18 suction chamber, 19 compression chamber, 20 vane slot, 24 discharge pipe, 25 oil supply cover, 26 oil supply path, 27 vane pump suction port, 30 throttle hole, 31 ... Communication hole, 32, 36 ... Centrifugal pump, 34 ... Pipe for oil supply, 35 ... Support member, 40 ... Horizontal rotary compressor, 41 ... Motor part, 42 ... Compression mechanism part.

Claims (9)

底部に潤滑油を貯留した密閉容器内に、作動流体を圧縮する圧縮機構部と、この圧縮機構部にシャフトを介して接続したモータ部とを収納し、前記潤滑油を前記圧縮機構部の摺動部に供給する給油手段を備えた横形ロータリ圧縮機において、
前記給油手段は、圧縮機構部側の底部の潤滑油を前記圧縮機構部の摺動部に供給する第１の給油手段と、前記モータ部側の底部の潤滑油を前記圧縮機構部の摺動部に供給する第２の給油手段とを有する横形ロータリ圧縮機。A compression mechanism for compressing the working fluid and a motor connected to the compression mechanism via a shaft are housed in a closed container storing lubricating oil at the bottom, and the lubricating oil slides on the compression mechanism. In a horizontal rotary compressor provided with oiling means for supplying to a moving part,
The lubricating means includes a first lubricating means for supplying a lubricating oil at a bottom of the compression mechanism to a sliding portion of the compression mechanism, and a lubricating oil at a bottom of the motor for sliding the compression mechanism. And a second oil supply means for supplying the oil to the section. 前記第１の給油手段は、前記圧縮機構部のシリンダ内を前記シャフトの回転に伴って偏心回転するローラに追随して往復動するベーンの下部に密閉的に形成されたベーンポンプ室と、前記密閉容器の底部の潤滑油を前記ベーンポンプ室へ吸入する吸入口と、前記ベーンポンプ室から前記圧縮機構部の摺動部に潤滑油を供給する給油路とを備えたベーンポンプを用いて構成したことを特徴とする請求項１に記載の横形ロータリ圧縮機。The first oil supply means includes a vane pump chamber hermetically formed below a vane that reciprocates in a cylinder of the compression mechanism following a roller that is eccentrically rotated with the rotation of the shaft. A vane pump having a suction port for sucking lubricating oil at the bottom of the container into the vane pump chamber and an oil supply path for supplying lubricating oil from the vane pump chamber to a sliding portion of the compression mechanism section is provided. The horizontal rotary compressor according to claim 1, wherein 前記圧縮機構部は第１および第２の圧縮部よりなる２組の圧縮部を備えて構成され、前記第１の圧縮部は、前記シャフトを軸支する主軸受、第１のシリンダ、仕切板、第１のローラおよび第１のベーンを備えて構成され、前記第２の圧縮部は、前記仕切板、第２のシリンダ、前記シャフトを軸支する副軸受、第２のローラおよび第２のベーンを備えて構成され、前記ベーンポンプは前記第２の圧縮部側に形成したことを特徴とする請求項２に記載の横形ロータリ圧縮機。The compression mechanism section includes two sets of compression sections including a first and a second compression section. The first compression section includes a main bearing that supports the shaft, a first cylinder, and a partition plate. , A first roller and a first vane, the second compressing section includes a partition plate, a second cylinder, an auxiliary bearing for supporting the shaft, a second roller, and a second roller. The horizontal rotary compressor according to claim 2, wherein the compressor is provided with a vane, and the vane pump is formed on the second compression unit side. 前記ベーンポンプ室への吸入口は、前記圧縮機構部を構成するシリンダおよび端板の当接面を含む少なくとも一方側に穿った凹溝により形成したことを特徴とする請求項２に記載の横形ロータリ圧縮機。The horizontal rotary according to claim 2, wherein the suction port to the vane pump chamber is formed by a concave groove formed on at least one side including a contact surface of a cylinder and an end plate that constitute the compression mechanism. Compressor. 前記ベーンポンプ室から前記圧縮機構部の摺動部に潤滑油を供給する給油路の一部を、プレス加工により給油路を形作る溝を有する板で構成した給油用カバー２５を前記端板の側面側に固定することにより形成したことを特徴とする請求項２に記載の横形ロータリ圧縮機。A part of the oil supply passage for supplying the lubricating oil from the vane pump chamber to the sliding portion of the compression mechanism is formed by a plate having a groove having an oil supply passage formed by press working. 3. The horizontal rotary compressor according to claim 2, wherein the horizontal rotary compressor is formed by fixing the rotary compressor. 前記圧縮機構部を構成するモータ部側の端板により圧縮機構部側とモータ部側とを仕切り、前記端板の下部に圧縮機構部側とモータ部側とを連通する連通穴を設け、前記圧縮機構部の圧縮室の吐出口を前記モータ部側に連通するように設け、前記主軸受の上部に圧縮機構部側とモータ部側とを連通する絞り穴を設け、前記圧縮機構部側に圧縮機の外へ前記作動流体を吐出する吐出パイプを設けたことを特徴とする請求項１または２に記載の横形ロータリ圧縮機。The compression mechanism section side and the motor section side are partitioned by an end plate on the motor section side constituting the compression mechanism section, and a communication hole communicating the compression mechanism section side and the motor section side is provided below the end plate, A discharge port of a compression chamber of the compression mechanism is provided so as to communicate with the motor section side, and a throttle hole communicating the compression mechanism section and the motor section is provided above the main bearing, and a throttle hole is provided on the compression mechanism section side. 3. The horizontal rotary compressor according to claim 1, wherein a discharge pipe for discharging the working fluid is provided outside the compressor. 前記第２の給油手段は、前記密閉容器内を吐出圧とすると共に、一側端部が前記シャフトの貫通穴のモータ部側の開口に連通し且つ他側端部が前記密閉容器の底部に延びている給油用パイプを備えて構成したことを特徴とする請求項１に記載の横形ロータリ圧縮機。The second oil supply means is configured such that the inside of the closed container is set to a discharge pressure, one end of the second oil supply unit communicates with the opening of the through hole of the shaft on the motor unit side, and the other end is connected to the bottom of the closed container. 2. The horizontal rotary compressor according to claim 1, wherein the compressor is provided with an extending oil supply pipe. 前記給油用パイプを支持する支持部材に前記給油パイプを圧縮機全体の回転に伴って回転可能に取付けたことを特徴とする請求項７に記載の横形ロータリ圧縮機。The horizontal rotary compressor according to claim 7, wherein the oil supply pipe is rotatably attached to a support member that supports the oil supply pipe in accordance with rotation of the entire compressor. 前記圧縮機構部の摺動部に連通する貫通穴を前記シャフトに設け、前記貫通穴の圧縮機構部側およびモータ部側の少なくとも一方の端部に遠心ポンプを設けたことを特徴とする請求項１から８の何れかに記載の横形ロータリ圧縮機。A through hole communicating with a sliding portion of the compression mechanism portion is provided in the shaft, and a centrifugal pump is provided at at least one end of the through hole on the compression mechanism side and the motor side. 9. The horizontal rotary compressor according to any one of 1 to 8.
JP2003119469A 2003-04-24 2003-04-24 Horizontal rotary compressor Expired - Fee Related JP4223858B2 (en)

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CNA2004100082027A CN1540166A (en) 2003-04-24 2004-03-01 Horizontal rotary commpressor

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Cited By (4)

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KR101045672B1 (en) 2009-06-22 2011-06-30 히다치 어플라이언스 가부시키가이샤 Horizontal arrangement type closed type compressor
WO2020080020A1 (en) * 2018-10-15 2020-04-23 サンデンホールディングス株式会社 Compressor
WO2023286943A1 (en) * 2021-07-15 2023-01-19 삼성전자주식회사 Horizontal type rotary compressor and home appliance including same
US11953001B2 (en) 2021-07-15 2024-04-09 Samsung Electronics Co., Ltd. Horizontal type rotary compressor and home appliance including the same

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CN105402135A (en) * 2014-08-18 2016-03-16 珠海格力节能环保制冷技术研究中心有限公司 Rotary compressor
KR20180014615A (en) 2016-08-01 2018-02-09 엘지전자 주식회사 Clothes treatment apparatus
CN106907323B (en) * 2017-04-26 2018-09-11 广东美芝精密制造有限公司 Compressor
CN107288881B (en) * 2017-07-06 2020-03-13 珠海格力节能环保制冷技术研究中心有限公司 Pump body assembly, fluid machine and heat exchange equipment
JP6967994B2 (en) * 2018-02-23 2021-11-17 本田技研工業株式会社 Lubricating oil supply device
CN109654019A (en) * 2019-02-21 2019-04-19 浙江博阳压缩机有限公司 A kind of horizontal rotary compressor

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101045672B1 (en) 2009-06-22 2011-06-30 히다치 어플라이언스 가부시키가이샤 Horizontal arrangement type closed type compressor
WO2020080020A1 (en) * 2018-10-15 2020-04-23 サンデンホールディングス株式会社 Compressor
WO2023286943A1 (en) * 2021-07-15 2023-01-19 삼성전자주식회사 Horizontal type rotary compressor and home appliance including same
US11953001B2 (en) 2021-07-15 2024-04-09 Samsung Electronics Co., Ltd. Horizontal type rotary compressor and home appliance including the same

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