WO2016031129A1 - Rotary compressor and refrigeration cycle device - Google Patents

Rotary compressor and refrigeration cycle device Download PDF

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WO2016031129A1
WO2016031129A1 PCT/JP2015/003675 JP2015003675W WO2016031129A1 WO 2016031129 A1 WO2016031129 A1 WO 2016031129A1 JP 2015003675 W JP2015003675 W JP 2015003675W WO 2016031129 A1 WO2016031129 A1 WO 2016031129A1
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bearing
peripheral
rotary compressor
rotary
value
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PCT/JP2015/003675
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French (fr)
Japanese (ja)
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平山 卓也
ジャフェット フェルディ モナスリ
木村 茂喜
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東芝キヤリア株式会社
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Priority to JP2014172415A priority Critical patent/JP6262101B2/en
Priority to JP2014-172415 priority
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Publication of WO2016031129A1 publication Critical patent/WO2016031129A1/en

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00Combinations 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00

Abstract

[Problem] To provide a rotary compressor in which a rotation shaft is axially supported by at least three bearing portions, and a refrigeration cycle device, the rotary compressor being capable of easily aligning the bearing portions and suppressing the occurrence of tilting and whirling of the rotation shaft. [Solution] A compression mechanism portion has at least three cylinders arranged in an axial direction of a rotation shaft, a blocking member blocking both ends of the cylinders and forming a cylinder chamber in each of the cylinders, and a roller that eccentrically rotates in the cylinder chamber. The rotation shaft is axially supported by bearing portions provided to at least three of the blocking members. When the clearance of a slide part between an inner circumferential surface of the bearing portion and an outer circumferential surface of the rotation shaft is "C", and the length in the axial direction between the inner circumferential surface of the bearing portion and the outer circumferential surface of the rotation shaft is "L", the value of "C/L" of the bearing portion closest to an electrical motor unit is smaller than the values of "C/L" of the other bearing portions.

Description

回転式圧縮機及び冷凍サイクル装置Rotary compressor and refrigeration cycle apparatus
 本発明の実施形態は、回転式圧縮機及び冷凍サイクル装置に関する。 Embodiments of the present invention relate to a rotary compressor and a refrigeration cycle apparatus.
 従来、電動機部とこの電動機部に連結された回転軸により駆動される圧縮機構部とが密閉ケース内に収容され、圧縮機構部でガス冷媒等の作動流体を圧縮する回転式圧縮機が知られている。このような回転式圧縮機のなかには、圧縮機構部に、回転軸の軸方向に配列された三つのシリンダと、回転軸を軸支する少なくとも三つの軸受部とを有するものが知られている(下記特許文献1、2参照)。 Conventionally, there has been known a rotary compressor in which an electric motor unit and a compression mechanism unit driven by a rotating shaft connected to the electric motor unit are housed in a hermetically sealed case, and a working fluid such as a gas refrigerant is compressed by the compression mechanism unit. ing. Among such rotary compressors, those having three cylinders arranged in the axial direction of the rotating shaft and at least three bearing portions that support the rotating shaft are known in the compression mechanism section ( See Patent Documents 1 and 2 below).
特開2012-122400号公報JP 2012-122400 A 特許第4594302号公報Japanese Patent No. 4594302
 しかしながら、圧縮機構部に三つのシリンダと三つ以上の軸受部とを設けた場合、三つ以上の軸受部を調芯することは容易でなく、回転式圧縮機の組立に多大な手間がかかる。 However, when three cylinders and three or more bearing parts are provided in the compression mechanism, it is not easy to align the three or more bearing parts, and it takes a lot of time to assemble the rotary compressor. .
また、三つのシリンダを設けることにより回転軸の長さが長くなるため、回転軸の曲がりや変形等が生じやすくなる。 Moreover, since the length of the rotating shaft is increased by providing three cylinders, the rotating shaft is likely to be bent or deformed.
 本発明の実施形態の目的は、少なくとも三つの軸受部を用いて回転軸を軸支する回転式圧縮機において、それらの軸受部の調芯を容易に行えるようにし、しかも、回転軸の傾きや振れ回りの発生を抑制することができる回転式圧縮機及び冷凍サイクル装置を提供することにある。 An object of an embodiment of the present invention is to make it easy to align the bearings in a rotary compressor that supports a rotating shaft using at least three bearings, and to An object of the present invention is to provide a rotary compressor and a refrigeration cycle apparatus that can suppress the occurrence of swinging.
 実施形態の回転式圧縮機は、電動機部とこの電動機部に連結された回転軸により駆動される圧縮機構部とが密閉ケース内に収容され、圧縮機構部で作動流体を圧縮する回転式圧縮機において、圧縮機構部は、回転軸の軸方向に配列されて回転軸を囲む少なくとも三つのシリンダと、各シリンダの両端を閉塞して各シリンダ内にシリンダ室を形成する閉塞部材と、回転軸の各シリンダ室内に位置する部分に設けられた偏心部と、偏心部に嵌合されて回転軸の回転に伴い各シリンダ室内で偏心回転するローラと、各シリンダ室内を周方向に吸込室と圧縮室とに二分するブレードとを有し、回転軸は閉塞部材の少なくとも三つに設けられた軸受部により軸支され、軸受部の内周面と回転軸の外周面との間の摺動部分のクリアランスを“C”、軸受部の内周面と回転軸の外周面との間の摺動部分の軸方向の長さを“L”とした場合、電動機部の最も近くに位置する軸受部の“C/L”の値を、他の軸受部の“C/L”の値より小さくしたことを特徴とする。 The rotary compressor according to the embodiment is a rotary compressor in which an electric motor unit and a compression mechanism unit driven by a rotary shaft connected to the electric motor unit are housed in a hermetically sealed case, and the working fluid is compressed by the compression mechanism unit. The compression mechanism section includes at least three cylinders that are arranged in the axial direction of the rotation shaft and surround the rotation shaft, a closing member that closes both ends of each cylinder to form a cylinder chamber in each cylinder, An eccentric portion provided in a portion located in each cylinder chamber, a roller that is fitted to the eccentric portion and rotates eccentrically in each cylinder chamber as the rotary shaft rotates, and a suction chamber and a compression chamber in the circumferential direction in each cylinder chamber The rotary shaft is pivotally supported by a bearing portion provided on at least three of the closing members, and a sliding portion between the inner peripheral surface of the bearing portion and the outer peripheral surface of the rotary shaft is provided. Clearance “C”, bearing When the axial length of the sliding portion between the inner peripheral surface of the motor and the outer peripheral surface of the rotary shaft is “L”, the value of “C / L” of the bearing portion located closest to the motor portion is Further, the value is smaller than the value of “C / L” of other bearing portions.
 また、実施形態の冷凍サイクル装置は、上記記載の回転式圧縮機と、前記回転式圧縮機に接続される凝縮器と、前記凝縮器に接続される膨張装置と、前記膨張装置と前記回転式圧縮機との間に接続される蒸発器とを備えることを特徴とする。 Moreover, the refrigeration cycle apparatus according to the embodiment includes the rotary compressor described above, a condenser connected to the rotary compressor, an expansion device connected to the condenser, the expansion device, and the rotary type. And an evaporator connected to the compressor.
 これにより、少なくとも三つの軸受部を用いて回転軸を軸支する回転式圧縮機において、それらの軸受部の調芯を容易に行えるようにし、しかも、回転軸の傾きや振れ回りの発生を抑制することができる回転式圧縮機及び冷凍サイクル装置を得ることができる。 As a result, in a rotary compressor that supports a rotating shaft using at least three bearing portions, it is possible to easily align the bearing portions, and to prevent the rotation shaft from tilting and swinging. A rotary compressor and a refrigeration cycle apparatus can be obtained.
断面で示した回転式圧縮機を含む冷凍サイクル装置の構成図である。It is a block diagram of the refrigerating-cycle apparatus containing the rotary compressor shown in the cross section. シリンダの部分を示す水平断面図である。It is a horizontal sectional view showing a portion of a cylinder. 軸受部の内周面と回転軸の外周面との間のクリアランス“C”についての説明図である。It is explanatory drawing about clearance "C" between the internal peripheral surface of a bearing part, and the outer peripheral surface of a rotating shaft.
 実施形態について、図面に基づいて説明する。図1は冷凍サイクル装置1の全体構成を示しており、この冷凍サイクル装置1は、圧縮機本体2とアキュムレータ3とを有している。また、作動流体であるガス冷媒を圧縮する回転式圧縮機4と、圧縮機本体2に接続されて圧縮機本体2から吐出された高圧・高温のガス冷媒を凝縮して液冷媒にする凝縮器5と、凝縮器5に接続されて液冷媒を減圧する膨張装置6と、膨張装置6とアキュムレータ3との間に接続されて膨張した液冷媒を蒸発させる蒸発器7とを有している。アキュムレータ3と圧縮機本体2とは、ガス冷媒が流れる吸込流路8により接続されている。 Embodiments will be described with reference to the drawings. FIG. 1 shows the overall configuration of a refrigeration cycle apparatus 1, which has a compressor body 2 and an accumulator 3. Further, a rotary compressor 4 that compresses a gas refrigerant that is a working fluid, and a condenser that is connected to the compressor main body 2 and condenses the high-pressure and high-temperature gas refrigerant discharged from the compressor main body 2 into a liquid refrigerant. 5, an expansion device 6 connected to the condenser 5 for decompressing the liquid refrigerant, and an evaporator 7 connected between the expansion device 6 and the accumulator 3 for evaporating the expanded liquid refrigerant. The accumulator 3 and the compressor body 2 are connected by a suction flow path 8 through which a gas refrigerant flows.
 圧縮機本体2は、円筒状に形成された密閉ケース9を有し、密閉ケース9内には、上方側に位置する電動機部10と、電動機部10に連結されて上下方向に中心線を有する回転軸11と、回転軸11を介して電動機部10により駆動される圧縮機構部12とが収容されている。 The compressor body 2 has a sealed case 9 formed in a cylindrical shape. In the sealed case 9, an electric motor unit 10 located on the upper side and a center line in the vertical direction are connected to the electric motor unit 10. The rotating shaft 11 and the compression mechanism part 12 driven by the electric motor part 10 via the rotating shaft 11 are accommodated.
 電動機部10は、回転軸11が固定された回転子13と、密閉ケース9の内周部に固定されて回転子13を囲む位置に配置された固定子14とを有している。回転子13には永久磁石(図示せず)が設けられ、固定子14には通電用のコイル(図示せず)が巻かれている。コイルに通電されることにより、回転子13と回転軸11とが一体に回転する。 The electric motor unit 10 includes a rotor 13 to which the rotating shaft 11 is fixed, and a stator 14 that is fixed to the inner peripheral portion of the sealed case 9 and disposed at a position surrounding the rotor 13. The rotor 13 is provided with a permanent magnet (not shown), and a current-carrying coil (not shown) is wound around the stator 14. When the coil is energized, the rotor 13 and the rotating shaft 11 rotate integrally.
 圧縮機構部12は、ガス冷媒を圧縮する部分であり、回転軸11の軸方向に配列された三つのシリンダ15a、15b、15cを有している。各シリンダ15a、15b、15cにおける回転軸11の軸方向に沿った両端は閉塞部材(主軸受16、第1仕切板17、第2仕切板18、副軸受19)により閉塞され、両端を閉塞された各シリンダ15a、15b、15c内にシリンダ室20a、20b、20cが形成されている。これらの閉塞部材(主軸受16、第1仕切板17、第2仕切板18、副軸受19)には回転軸11が貫通されており、回転軸11は、主軸受16に設けられた軸受部16aと、第2仕切板18に設けられた軸受部18aと、副軸受19に設けられた軸受部19aとにより軸支されている。なお、第1仕切板17にも軸受部を設けても良く、閉塞部材の少なくとも三つに軸受部を設ければよい。 The compression mechanism unit 12 is a portion that compresses the gas refrigerant, and includes three cylinders 15 a, 15 b, and 15 c arranged in the axial direction of the rotary shaft 11. Both ends of each cylinder 15a, 15b, 15c along the axial direction of the rotary shaft 11 are closed by blocking members (main bearing 16, first partition plate 17, second partition plate 18, sub bearing 19), and both ends are closed. Cylinder chambers 20a, 20b, and 20c are formed in the cylinders 15a, 15b, and 15c. The rotating shaft 11 is penetrated by these closing members (the main bearing 16, the first partition plate 17, the second partition plate 18, and the auxiliary bearing 19), and the rotating shaft 11 is a bearing portion provided in the main bearing 16. 16 a, a bearing portion 18 a provided on the second partition plate 18, and a bearing portion 19 a provided on the auxiliary bearing 19. In addition, a bearing part may be provided also in the 1st partition plate 17, and what is necessary is just to provide a bearing part in at least three of the closure members.
 回転軸11における各シリンダ室20a、20b、20c内に位置する部分には偏心部21a、21b、21cが設けられ、各偏心部21a、21b、21cにはローラ22a、22b、22cが嵌合されている。各ローラ22a、22b、22cは、回転軸11の回転時に外周面を各シリンダ15a、15b、15cの内周面に油膜を介して線接触させながら偏心回転するように配置されている。 Eccentric portions 21a, 21b, and 21c are provided in portions of the rotary shaft 11 located in the cylinder chambers 20a, 20b, and 20c, and rollers 22a, 22b, and 22c are fitted into the eccentric portions 21a, 21b, and 21c. ing. Each roller 22a, 22b, 22c is arranged to rotate eccentrically while the outer peripheral surface is in line contact with the inner peripheral surface of each cylinder 15a, 15b, 15c via an oil film when the rotary shaft 11 rotates.
 また、各シリンダ室20a、20b、20cには、各シリンダ室20a、20b、20c内を周方向に沿って吸込室38と圧縮室39とに二分するブレード25a、25b、25cが設けられている。なお、吸込室38と圧縮室39については後述する図2において説明する。 Each cylinder chamber 20a, 20b, 20c is provided with blades 25a, 25b, 25c that bisect the inside of each cylinder chamber 20a, 20b, 20c into a suction chamber 38 and a compression chamber 39 along the circumferential direction. . The suction chamber 38 and the compression chamber 39 will be described later with reference to FIG.
 主軸受16には、シリンダ室20a内で圧縮されたガス冷媒が吐出される吐出ポート26と、吐出ポート26を開閉する吐出弁27とが設けられている。また、主軸受16には、吐出ポート26から吐出されたガス冷媒が流入する主軸受側マフラ28が取付けられている。主軸受側マフラ28内に流入したガス冷媒は、主軸受側マフラ28に形成された流出口29から密閉ケース9内に流出するようになっている。 The main bearing 16 is provided with a discharge port 26 through which the gas refrigerant compressed in the cylinder chamber 20a is discharged, and a discharge valve 27 for opening and closing the discharge port 26. Further, a main bearing side muffler 28 into which the gas refrigerant discharged from the discharge port 26 flows is attached to the main bearing 16. The gas refrigerant that has flowed into the main bearing side muffler 28 flows into the sealed case 9 from an outlet 29 formed in the main bearing side muffler 28.
 第1仕切板17には、シリンダ室20b内で圧縮されたガス冷媒が吐出される吐出ポート30と、吐出ポート30を開閉する吐出弁31とが設けられている。第1仕切板17内には、吐出ポート30から吐出されたガス冷媒が流入する仕切板内空間32が形成されている。仕切板内空間32内と主軸受側マフラ28内とは連通路33により連通され、吐出ポート30から吐出されて仕切板内空間32内に流入したガス冷媒は、連通路33内を通って主軸受側マフラ28内に流入するようになっている。 The first partition plate 17 is provided with a discharge port 30 through which the gas refrigerant compressed in the cylinder chamber 20b is discharged, and a discharge valve 31 for opening and closing the discharge port 30. In the first partition plate 17, a partition plate inner space 32 into which the gas refrigerant discharged from the discharge port 30 flows is formed. The inside of the partition plate space 32 and the inside of the main bearing side muffler 28 are communicated with each other through the communication passage 33, and the gas refrigerant discharged from the discharge port 30 and flowing into the partition plate space 32 passes through the communication passage 33. It flows into the bearing side muffler 28.
 副軸受19には、シリンダ室20c内で圧縮されたガス冷媒が吐出される吐出ポート34と、吐出ポート34を開閉する吐出弁35とが設けられている。また、副軸受19には、吐出ポート34から吐出されたガス冷媒が流入する副軸受側マフラ36が取付けられている。副軸受側マフラ36内と仕切板内空間32とは、図示しない連通路により連通され、吐出ポート34から吐出された副軸受側マフラ36内に流入したガス冷媒は、仕切板内空間32を経由して主軸受側マフラ28内に流入するようになっている。 The auxiliary bearing 19 is provided with a discharge port 34 through which the gas refrigerant compressed in the cylinder chamber 20c is discharged, and a discharge valve 35 that opens and closes the discharge port 34. Further, a sub bearing side muffler 36 into which the gas refrigerant discharged from the discharge port 34 flows is attached to the sub bearing 19. The sub-bearing side muffler 36 and the partition plate space 32 communicate with each other through a communication passage (not shown), and the gas refrigerant discharged from the discharge port 34 into the sub-bearing side muffler 36 passes through the partition plate space 32. Then, it flows into the main bearing side muffler 28.
 図2は、圧縮機構部12の一部であるシリンダ15aの部分を示す水平断面図である。 FIG. 2 is a horizontal sectional view showing a portion of the cylinder 15a which is a part of the compression mechanism section 12. As shown in FIG.
シリンダ15aにはブレード溝37が形成され、このブレード溝37に往復移動可能にブレード25aが収容されている。ブレード25aは、先端部をローラ22aの外周面に当接させるように付勢されており、ブレード25aの先端部がローラ22aの外周面に当接されることによりシリンダ室20a内が周方向に吸込室38と圧縮室39とに二分されている。吸込室38には吸込流路8が連通され、圧縮室39には吐出ポート26が連通されている。 A blade groove 37 is formed in the cylinder 15a, and the blade 25a is accommodated in the blade groove 37 so as to be reciprocally movable. The blade 25a is urged so that the tip end abuts against the outer peripheral surface of the roller 22a. The tip of the blade 25a abuts against the outer peripheral surface of the roller 22a, so that the inside of the cylinder chamber 20a extends in the circumferential direction. It is divided into a suction chamber 38 and a compression chamber 39. The suction flow path 8 is communicated with the suction chamber 38, and the discharge port 26 is communicated with the compression chamber 39.
 他のシリンダ15b、15cの部分の構成もシリンダ15aの部分の構成と同じであり、各シリンダ室20b、20cは各ブレード25b、25cにより吸込室38と圧縮室39とに二分されている。 The configuration of the other cylinders 15b and 15c is the same as the configuration of the cylinder 15a, and each cylinder chamber 20b and 20c is divided into a suction chamber 38 and a compression chamber 39 by each blade 25b and 25c.
 図3は、軸受部16aの内周面と回転軸11の外周面との間のクリアランス“C”についての説明図である。主軸受16の軸受部16aの内径寸法を“D”、回転軸11の軸受部16aに軸支された部分の外形寸法を“d”とした場合、クリアランス“C”は、“C=D-d”と表される。図示は省略するが、第2仕切板18の軸受部18aの内周面と回転軸11の外周面との間のクリアランス“C”、副軸受19の軸受部19aの内周面と回転軸11の外周面との間のクリアランス“C”も同様に表される。 FIG. 3 is an explanatory view of the clearance “C” between the inner peripheral surface of the bearing portion 16 a and the outer peripheral surface of the rotary shaft 11. When the inner diameter dimension of the bearing portion 16a of the main bearing 16 is "D" and the outer dimension of the portion pivotally supported by the bearing portion 16a of the rotary shaft 11 is "d", the clearance "C" is "C = D- d ". Although not shown, the clearance “C” between the inner peripheral surface of the bearing portion 18 a of the second partition plate 18 and the outer peripheral surface of the rotary shaft 11, the inner peripheral surface of the bearing portion 19 a of the auxiliary bearing 19, and the rotary shaft 11. The clearance “C” between the outer peripheral surface and the outer peripheral surface is similarly expressed.
 ここで、回転軸11を軸支する三つの軸受部16a、18a、19aにおいて、上述したようにクリアランスを“C”とし、さらに、それらの軸受部16a、18a、19aの内周面と回転軸11の外周面との間の摺動部分の軸方向の長さを“L”(図1参照)とした場合、電動機部10の最も近くに位置する軸受部16aの“C/L”の値は、他の軸受部18a、19aの“C/L”の値より小さく設定されている。 Here, in the three bearing portions 16a, 18a, and 19a that support the rotating shaft 11, the clearance is set to “C” as described above, and the inner peripheral surfaces of these bearing portions 16a, 18a, and 19a and the rotating shaft 11 is the value of “C / L” of the bearing portion 16a located closest to the electric motor portion 10 when the length in the axial direction of the sliding portion between the outer peripheral surface 11 and the outer peripheral surface 11 is “L” (see FIG. 1). Is set smaller than the value of “C / L” of the other bearing portions 18a and 19a.
 また、三つの軸受部16a、18a、19aのうち、両端に位置する軸受部16a、19aの“C/L”の値は、その間に位置する軸受部18aの“C/L”の値より小さく設定されている。 Of the three bearing portions 16a, 18a and 19a, the “C / L” value of the bearing portions 16a and 19a located at both ends is smaller than the “C / L” value of the bearing portion 18a located therebetween. Is set.
 図1に戻って説明する。副軸受19における電動機部10から離れた側の端部には、リング状の溝40が形成されている。この溝40が形成されていることにより、電動機部10から最も離れて位置する軸受部19aの回転軸11との摺動面における電動機部10から離れた端部側の剛性を、電動機部10の最も近くに位置する軸受部16aの回転軸11との摺動面における電動機部10に近い端部側の剛性より、小さく設定している。 Referring back to FIG. A ring-shaped groove 40 is formed at the end of the auxiliary bearing 19 on the side away from the motor unit 10. By forming the groove 40, the rigidity of the end portion side away from the motor unit 10 on the sliding surface with the rotating shaft 11 of the bearing unit 19a located farthest from the motor unit 10 is reduced. The rigidity is set smaller than the rigidity on the end side near the motor unit 10 on the sliding surface with the rotating shaft 11 of the bearing unit 16a located closest.
 つぎに、図2に戻って、ローラ22aの内周面と偏心部21aの外周面との間の嵌合部分のクリアランス“C´”について説明する。ローラ22aの内径寸法を“D´”、偏心部21aの外形寸法を“d´”とした場合、クリアランス“C´”は、“C´=D´-d´”と表される。図示は省略するが、ローラ22bの内周面と偏心部21bの外周面との間の嵌合部分のクリアランス“C´”、ローラ22cの内周面と偏心部21cの外周面との間の嵌合部分のクリアランス“C´”も同様に表される。 Next, returning to FIG. 2, the clearance “C ′” at the fitting portion between the inner peripheral surface of the roller 22a and the outer peripheral surface of the eccentric portion 21a will be described. When the inner diameter of the roller 22a is “D ′” and the outer dimension of the eccentric portion 21a is “d ′”, the clearance “C ′” is expressed as “C ′ = D′−d ′”. Although not shown, the clearance “C ′” of the fitting portion between the inner peripheral surface of the roller 22b and the outer peripheral surface of the eccentric portion 21b, and between the inner peripheral surface of the roller 22c and the outer peripheral surface of the eccentric portion 21c. The clearance “C ′” of the fitting portion is similarly expressed.
 ここで、ローラ22a、22b、22cと偏心部21a、21b、21cとの嵌合部分のクリアランスを上述のように“C´”とし、ローラ22a、22b、22cの内周面と偏心部21a、21b、21cの外周面との間の嵌合部分の軸方向の長さを“L´”(図1参照)とした場合、“C´/L´”の値は、上述した各軸受部16a、18a、19aの“C/L”の値より大きく設定されている。 Here, the clearance of the fitting portion between the rollers 22a, 22b, and 22c and the eccentric portions 21a, 21b, and 21c is “C ′” as described above, and the inner peripheral surface of the rollers 22a, 22b, and 22c and the eccentric portion 21a, When the length in the axial direction of the fitting portion between the outer peripheral surfaces of 21b and 21c is “L ′” (see FIG. 1), the value of “C ′ / L ′” is the value of each bearing portion 16a described above. , 18a and 19a are set to be larger than the “C / L” value.
 このような構成において、この回転式圧縮機4においては、電動機部10に通電することにより回転軸11が回転子13と共に中心線回りに回転し、この回転により圧縮機構部12が駆動され、各シリンダ室20a、20b、20c内でガス冷媒が圧縮される。 In such a configuration, in the rotary compressor 4, when the electric motor unit 10 is energized, the rotary shaft 11 rotates around the center line together with the rotor 13, and the compression mechanism unit 12 is driven by this rotation, The gas refrigerant is compressed in the cylinder chambers 20a, 20b, and 20c.
 圧縮されたガス冷媒の圧力が設定圧に達すると、各吐出弁27、31、35が開弁され、ガス冷媒が各吐出ポート26、30、34から吐出される。各吐出ポート26、30、34から吐出されたガス冷媒は、直接主軸受側マフラ28内に流入し、又は、仕切板内空間32や副軸受側マフラ36内を経由して主軸受側マフラ28内に流入する。主軸受側マフラ28内に流入したガス冷媒は、流出口29から密閉ケース9内に流出する。 When the pressure of the compressed gas refrigerant reaches the set pressure, the discharge valves 27, 31, 35 are opened, and the gas refrigerant is discharged from the discharge ports 26, 30, 34. The gas refrigerant discharged from each of the discharge ports 26, 30, 34 flows directly into the main bearing side muffler 28, or passes through the partition plate inner space 32 and the auxiliary bearing side muffler 36, so that the main bearing side muffler 28. Flows in. The gas refrigerant that has flowed into the main bearing-side muffler 28 flows out from the outlet 29 into the sealed case 9.
 密閉ケース9内に流出したガス冷媒は、凝縮器5、膨張装置6、蒸発器7の順に流れて回転式圧縮機4に戻り、冷凍サイクル装置1での冷凍サイクルが実行される。 The gas refrigerant that has flowed into the sealed case 9 flows in the order of the condenser 5, the expansion device 6, and the evaporator 7, returns to the rotary compressor 4, and the refrigeration cycle in the refrigeration cycle apparatus 1 is executed.
 ここで、圧縮機構部12では、回転軸11は三つの軸受部16a、18a、19aにより軸支されている。これらの軸受部16a、18a、19aにおいて、クリアランス“C”と摺動部分の軸方向の長さ“L”から求められる“C/L”の値は、電動機部10の最も近くに位置する軸受部16aが、他の軸受部18a、19aより小さく設定されている。 Here, in the compression mechanism part 12, the rotating shaft 11 is pivotally supported by three bearing parts 16a, 18a, 19a. In these bearing portions 16 a, 18 a, and 19 a, the value of “C / L” obtained from the clearance “C” and the axial length “L” of the sliding portion is the bearing located closest to the motor portion 10. The part 16a is set smaller than the other bearing parts 18a and 19a.
 このため、軸受部16aが電動機部10の駆動時における回転軸11の傾きや振れ回りを最も有効に抑制することができ、電動機部10の駆動時における回転子13と固定子14との間のギャプを均一に保つことができる。これにより、電動機部10の回転効率を向上させることができ、しかも、回転軸11の回転に伴って発生する騒音や振動を低減することができる。 For this reason, the bearing part 16a can most effectively suppress the inclination and swinging of the rotating shaft 11 when the electric motor part 10 is driven, and between the rotor 13 and the stator 14 when the electric motor part 10 is driven. The gap can be kept uniform. Thereby, the rotation efficiency of the electric motor part 10 can be improved, and the noise and vibration which generate | occur | produce with rotation of the rotating shaft 11 can be reduced.
 また、他の軸受部18a、19aにおいて“C/L”が大きく設定されていることにより、各軸受部16a、18a、19aの調芯を容易に行えるようになり、回転式圧縮機4の組立性を向上させることができる。 Further, since “C / L” is set large in the other bearing portions 18a and 19a, the alignment of the respective bearing portions 16a, 18a and 19a can be easily performed, and the assembly of the rotary compressor 4 is facilitated. Can be improved.
 また、圧縮機構部12の両端に位置する軸受部16a、19aの“C/L”の値が、中間に位置する軸受部18aの“C/L”の値より小さく設定されている。このため、電動機部10の駆動時における回転軸11の傾きや振れ回りを抑制することができ、電動機部10の駆動時における回転子13と固定子14との間のギャップを均一に保つことができる。これにより、電動機部10の回転効率を向上させることができ、しかも、回転軸11が回転することに伴って発生する騒音や振動を低減することができる。 Also, the “C / L” values of the bearing portions 16a and 19a located at both ends of the compression mechanism portion 12 are set to be smaller than the “C / L” value of the bearing portion 18a located in the middle. For this reason, it is possible to suppress the tilt and swing of the rotating shaft 11 when the electric motor unit 10 is driven, and to keep the gap between the rotor 13 and the stator 14 uniform when the electric motor unit 10 is driven. it can. Thereby, the rotation efficiency of the electric motor part 10 can be improved, and the noise and vibration which generate | occur | produce with the rotating shaft 11 rotating can be reduced.
 また、中間に位置する軸受部18aの“C/L”が大きく設定されているので、圧縮負荷による回転軸11の変形や撓みをより多く許容することができ、回転式圧縮機4の信頼性や耐久性を高めることができる。 Further, since “C / L” of the bearing portion 18a located in the middle is set large, it is possible to allow more deformation and bending of the rotating shaft 11 due to the compression load, and the reliability of the rotary compressor 4 And durability can be increased.
 軸受部19a、16aの回転軸11との摺動面における剛性を比較すると、副軸受19にリング状の溝40を形成していることにより、軸受部19aの電動機部10から離れた端部側の剛性は、軸受部16aの電動機部10に近い端部側の剛性より小さく設定されている。 これにより、電動機部10の最も近くに位置する軸受部16aの摺動面において、電動機部10に近い端部側の剛性が大きいため、回転軸11の傾きや振れ回りを抑制することができる。一方、電動機部10から離れて位置する軸受部19aの摺動面において、電動機部10から離れた端部側の剛性が小さいため、回転軸11が傾きや振れ回りを生じても回転軸11や軸受部19aに無理な力が作用することが抑制され、回転式圧縮機4の信頼性や耐久性を高めることができる。 Comparing the rigidity of the sliding surfaces of the bearing portions 19a and 16a with the rotating shaft 11, the ring-side groove 40 is formed in the auxiliary bearing 19, so that the end portion side of the bearing portion 19a away from the motor portion 10 is provided. Is set to be smaller than the rigidity of the end portion side of the bearing portion 16a close to the electric motor portion 10. Thereby, since the rigidity of the end portion close to the electric motor unit 10 is large on the sliding surface of the bearing unit 16a located closest to the electric motor unit 10, it is possible to suppress the inclination and swinging of the rotating shaft 11. On the other hand, on the sliding surface of the bearing portion 19a located away from the motor portion 10, the rigidity on the end side away from the motor portion 10 is small, so even if the rotation shaft 11 is inclined or swung, the rotation shaft 11 or An unreasonable force is prevented from acting on the bearing portion 19a, and the reliability and durability of the rotary compressor 4 can be improved.
 つぎに、ローラ22a、22b、22cの内周面と偏心部21a、21b、21cの外周面との間の嵌合部分のクリアランス“C´”と、ローラ22a、22b、22cの内周面と偏心部21a、21b、21cの外周面との間の嵌合部分の軸方向の長さ“L´”とからなる “C´/L´”の値は、各軸受部16a、18a、19aの“C/L”の値より大きく設定されている。このため、回転軸11の傾きや撓みが発生した場合において、回転軸11が傾いてもローラ22a、22b、22cは傾きが抑制される。このため、ローラ22a、22b、22cの端面が主軸受16、第1仕切板17、第2仕切板18、副軸受19に接触することや、ブレード25a、25b、25cの先端部がローラ22a、22b、22cの外周面に当接しなくなることが防止され、回転式圧縮機の4の信頼性や耐久性を高めることができる。 Next, the clearance “C ′” of the fitting portion between the inner peripheral surfaces of the rollers 22a, 22b, and 22c and the outer peripheral surfaces of the eccentric portions 21a, 21b, and 21c, and the inner peripheral surfaces of the rollers 22a, 22b, and 22c, The value of “C ′ / L ′” including the axial length “L ′” between the outer peripheral surfaces of the eccentric portions 21a, 21b, and 21c is the value of each bearing portion 16a, 18a, and 19a. It is set larger than the value of “C / L”. Therefore, when the rotation shaft 11 is tilted or bent, the rollers 22a, 22b, and 22c are restrained from tilting even when the rotation shaft 11 is tilted. For this reason, the end surfaces of the rollers 22a, 22b, and 22c are in contact with the main bearing 16, the first partition plate 17, the second partition plate 18, and the auxiliary bearing 19, and the tips of the blades 25a, 25b, and 25c are the rollers 22a, The contact with the outer peripheral surfaces of 22b and 22c is prevented from being stopped, and the reliability and durability of the rotary compressor 4 can be improved.
 以上、本発明のいくつかの実施形態を説明したが、これらの実施形態は、例として提示したものであり、発明の範囲を限定することは意図していない。これらの実施形態は、その他の様々な形態で実施されることが可能であり、発明の要旨を逸脱しない範囲で、種々の省略、置き換え、変更を行うことができる。この実施形態やその変形は、発明の範囲や要旨に含まれると同様に、特許請求の範囲に記載された発明とその均等の範囲に含まれるものである。 Although several embodiments of the present invention have been described above, these embodiments are presented as examples and are not intended to limit the scope of the invention. These embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the scope of the invention. This embodiment and its modifications are included in the scope of the present invention and the gist thereof, and are also included in the invention described in the claims and the equivalent scope thereof.
 4…回転式圧縮機、5…凝縮機、6…膨張装置、7…蒸発器、9…密閉ケース、10…電動機部、11…回転軸、12…圧縮機構部、15a、15b、15c…シリンダ、16…主軸受(閉塞部材)、17…第1仕切板(閉塞部材)、18…第2仕切板(閉塞部材)、19…副軸受(閉塞部材)、20a、20b、20c…シリンダ室、21a、21b。21c…偏心部、22a、22b、22c…ローラ、25a、25b、25c…ブレード、38…吸込室、39…圧縮室 DESCRIPTION OF SYMBOLS 4 ... Rotary compressor, 5 ... Condenser, 6 ... Expansion device, 7 ... Evaporator, 9 ... Sealing case, 10 ... Electric motor part, 11 ... Rotating shaft, 12 ... Compression mechanism part, 15a, 15b, 15c ... Cylinder , 16 ... main bearing (closing member), 17 ... first partition plate (closing member), 18 ... second partition plate (closing member), 19 ... auxiliary bearing (closing member), 20a, 20b, 20c ... cylinder chamber, 21a, 21b. 21c ... eccentric part, 22a, 22b, 22c ... roller, 25a, 25b, 25c ... blade, 38 ... suction chamber, 39 ... compression chamber

Claims (6)

  1.  電動機部とこの電動機部に連結された回転軸により駆動される圧縮機構部とが密閉ケース内に収容され、前記圧縮機構部で作動流体を圧縮する回転式圧縮機において、前記圧縮機構部は、前記回転軸の軸方向に配列されて前記回転軸を囲む少なくとも三つのシリンダと、前記各シリンダの両端を閉塞して各シリンダ内にシリンダ室を形成する閉塞部材と、前記回転軸の前記各シリンダ室内に位置する部分に設けられた偏心部と、前記偏心部に嵌合されて前記回転軸の回転に伴い前記各シリンダ室内で偏心回転するローラと、前記各シリンダ室内を周方向に吸込室と圧縮室とに二分するブレードとを有し、前記回転軸は前記閉塞部材の少なくとも三つに設けられた軸受部により軸支され、前記軸受部の内周面と前記回転軸の外周面との間の摺動部分のクリアランスを“C”、前記軸受部の内周面と前記回転軸の外周面との間の摺動部分の軸方向の長さを“L”とした場合、前記電動機部の最も近くに位置する前記軸受部の“C/L”の値を、他の前記軸受部の“C/L”の値より小さくしたことを特徴とする回転式圧縮機。 In a rotary compressor in which an electric motor unit and a compression mechanism unit driven by a rotary shaft connected to the electric motor unit are housed in a hermetically sealed case, and the working fluid is compressed by the compression mechanism unit, the compression mechanism unit includes: At least three cylinders arranged in the axial direction of the rotating shaft and surrounding the rotating shaft; a closing member that closes both ends of each cylinder to form a cylinder chamber in each cylinder; and each cylinder of the rotating shaft An eccentric portion provided in a portion located in the chamber, a roller that is fitted in the eccentric portion and rotates eccentrically in each cylinder chamber as the rotary shaft rotates, and a suction chamber in the circumferential direction in each cylinder chamber; A blade that bisects the compression chamber, and the rotary shaft is pivotally supported by bearing portions provided on at least three of the closing members, and an inner peripheral surface of the bearing portion and an outer peripheral surface of the rotary shaft Slip When the clearance of the portion is “C” and the axial length of the sliding portion between the inner peripheral surface of the bearing portion and the outer peripheral surface of the rotary shaft is “L”, it is closest to the motor portion. A rotary compressor characterized in that the value of “C / L” of the bearing portion positioned is smaller than the value of “C / L” of the other bearing portion.
  2.  両端に位置する前記軸受部の“C/L”の値を、その中間に位置する前記軸受部の“C/L”より小さくしたことを特徴とする請求項1記載の回転式圧縮機。 2. The rotary compressor according to claim 1, wherein a value of “C / L” of the bearing portion located at both ends is made smaller than “C / L” of the bearing portion located in the middle thereof.
  3.  前記電動機部から最も離れて位置する前記軸受部の摺動面における前記電動機部から離れた端部側の剛性が、前記電動機部の最も近くに位置する前記軸受部の摺動面における前記電動機部に近い端部側の剛性より小さいことを特徴とする請求項1又は2記載の回転式圧縮機。 The rigidity of the sliding portion of the bearing portion located farthest from the motor portion is such that the rigidity on the end portion side away from the motor portion in the sliding surface of the bearing portion located farthest from the motor portion is the sliding portion of the bearing portion located closest to the motor portion. The rotary compressor according to claim 1, wherein the rotary compressor is smaller than the rigidity on the end side close to.
  4.  前記ローラの内周面と前記偏心部の外周面との間の嵌合部分のクリアランスを“C´”、前記ローラの内周面と前記偏心部の外周面との間の嵌合部分の軸方向の長さを“L´”とした場合、“C´/L´”の値を、各前記軸受部の“C/L”の値より大きくしたことを特徴とする請求項1又は2記載の回転式圧縮機。 The clearance of the fitting portion between the inner peripheral surface of the roller and the outer peripheral surface of the eccentric portion is “C ′”, and the shaft of the fitting portion between the inner peripheral surface of the roller and the outer peripheral surface of the eccentric portion The value of "C '/ L'" is made larger than the value of "C / L" of each of the bearing portions when the length in the direction is "L '". Rotary compressor.
  5.  前記ローラの内周面と前記偏心部の外周面との間の嵌合部分のクリアランスを“C´”、前記ローラの内周面と前記偏心部の外周面との間の嵌合部分の軸方向の長さを“L´”とした場合、“C´/L´”の値を、各前記軸受部の“C/L”の値より大きくしたことを特徴とする請求項3記載の回転式圧縮機。 The clearance of the fitting portion between the inner peripheral surface of the roller and the outer peripheral surface of the eccentric portion is “C ′”, and the shaft of the fitting portion between the inner peripheral surface of the roller and the outer peripheral surface of the eccentric portion The rotation according to claim 3, wherein when the length in the direction is "L '", the value of "C' / L '" is larger than the value of "C / L" of each of the bearing portions. Type compressor.
  6.  請求項1ないし5のいずれか一項に記載の回転式圧縮機と、前記回転式圧縮機に接続される凝縮器と、前記凝縮器に接続される膨張装置と、前記膨張装置と前記回転式圧縮機との間に接続される蒸発器とを備えることを特徴とする冷凍サイクル装置。 The rotary compressor according to any one of claims 1 to 5, a condenser connected to the rotary compressor, an expansion device connected to the condenser, the expansion device, and the rotary type An refrigeration cycle apparatus comprising: an evaporator connected to the compressor.
PCT/JP2015/003675 2014-08-27 2015-07-22 Rotary compressor and refrigeration cycle device WO2016031129A1 (en)

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