JP2020016203A - Compressor - Google Patents

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Publication number
JP2020016203A
JP2020016203A JP2018140866A JP2018140866A JP2020016203A JP 2020016203 A JP2020016203 A JP 2020016203A JP 2018140866 A JP2018140866 A JP 2018140866A JP 2018140866 A JP2018140866 A JP 2018140866A JP 2020016203 A JP2020016203 A JP 2020016203A
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Prior art keywords
piston
notch
cylinder bore
dead center
oil
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JP7010786B2 (en
Inventor
遵自 鈴木
Junji Suzuki
遵自 鈴木
啓愛 鈴木
Hiroyoshi Suzuki
啓愛 鈴木
修平 永田
Shuhei Nagata
修平 永田
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Hitachi Global Life Solutions Inc
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Hitachi Global Life Solutions Inc
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/126—Cylinder liners
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0284—Constructional details, e.g. reservoirs in the casing
    • F04B39/0292—Lubrication of pistons or cylinders

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Abstract

To provide a compressor having excellent reliability.SOLUTION: A compressor comprises a cylinder comprising a cylinder bore 2b provided with a cylindrical gap, and a piston 3 to be reciprocated in the gap. Lubricating oil is supplied between the cylinder bore and the piston. The cylinder bore comprises a first notch part 2c and a second notch part 2d opposed to each other across the gap.SELECTED DRAWING: Figure 3

Description

本発明は、圧縮機に関する。   The present invention relates to a compressor.

特許文献１の圧縮機は、ピストンに凹設した環状の給油溝２３ｅが、ピストンの下死点において、切欠き部７ｃから露出する位置関係になるように設定することにより、吸い込み工程時に下死点で切欠き部から給油溝に潤滑油が給油され、給油溝とシリンダボアとの間に油膜を形成することで圧縮時のシール性を向上している（００２５，図３）。   The compressor of Patent Literature 1 sets the annular oil supply groove 23e recessed in the piston so that the oil supply groove 23e is exposed from the notch 7c at the bottom dead center of the piston. At this point, lubricating oil is supplied from the notch to the oil supply groove, and an oil film is formed between the oil supply groove and the cylinder bore, thereby improving the sealing property during compression (0025, FIG. 3).

特開２００６−２８３７７０号公報JP 2006-283770 A

油膜には圧縮冷媒からの圧力がかかるため、圧縮時のピストンは油膜からの反力を受けるところ、特許文献１の圧縮機では、下死点においてピストンの給油溝２３ｅのうち上部のみが切欠き部７ｃを介して露出しており、その他の部分はシリンダボアに入り込んでいる。このため、吸い込み工程から圧縮工程に移った後、上死点に向かって移動することで給油溝の全周がシリンダボアに入り込むまでは、油膜は切欠き部分には形成されない。すると、ピストンにかかる油膜の反力は、ピストン上側が小さく下側が大きいアンバランスとなり、反力の合成力はピストンを上下方向に振れさせる方向に働く。   Since the pressure from the compressed refrigerant is applied to the oil film, the piston at the time of compression receives a reaction force from the oil film. However, in the compressor of Patent Document 1, only the upper part of the oil supply groove 23e of the piston is notched at the bottom dead center. The other portion is exposed through the portion 7c, and the other portion enters the cylinder bore. Therefore, after moving from the suction process to the compression process, the oil film is not formed in the notched portion until the entire circumference of the oil supply groove enters the cylinder bore by moving toward the top dead center. Then, the reaction force of the oil film applied to the piston becomes unbalanced on the upper side of the piston and smaller on the lower side, and the resultant force of the reaction force acts in the direction of causing the piston to swing up and down.

ピストンの上下方向の振れは、圧縮機全体の振動を増加させ、騒音増加につながる。また、振れが過大になると、ピストンとシリンダボア、ピストンに運転力を伝達するコンロッドやピストンピン、シャフトなどといった各部材同士の磨耗を発生し得る。磨耗は熱損失となり、圧縮機の性能低下の原因であると共に、圧縮機の信頼性を損なう虞がある。   The vertical run-out of the piston increases the vibration of the entire compressor, which leads to an increase in noise. Further, when the run-out is excessive, wear of each member such as a piston and a cylinder bore, a connecting rod for transmitting an operating force to the piston, a piston pin, a shaft, and the like may occur. Wear results in heat loss, which causes a decrease in compressor performance, and may reduce the reliability of the compressor.

上記事情に鑑みてなされた本発明は、
円筒状の空隙が設けられたシリンダボアを有するシリンダと、
該空隙内を往復動するピストンと、を備え、
前記シリンダボアと前記ピストンとの間に潤滑油が供給される圧縮機であって、
前記シリンダボアは、前記空隙を挟んで互いに対向する第１切欠き部及び第２切欠き部を有することを特徴とする。 The present invention made in view of the above circumstances,
A cylinder having a cylinder bore provided with a cylindrical gap,
A piston reciprocating in the gap,
A compressor in which lubricating oil is supplied between the cylinder bore and the piston,
The cylinder bore has a first notch and a second notch facing each other across the gap.

実施例１の１密閉型電動圧縮機の縦断面図。FIG. 1 is a longitudinal sectional view of a hermetic electric compressor according to a first embodiment. 実施例１のピストンが圧縮工程の下死点近傍位置にあるときの要部断面図。FIG. 3 is a cross-sectional view of a main part when the piston of the first embodiment is at a position near the bottom dead center in the compression process. 図２のA-A断面視で、圧縮時にピストンにかかる油膜反力を表した模式図。FIG. 3 is a schematic view showing an oil film reaction force applied to a piston at the time of compression in a cross-sectional view taken along line AA of FIG. 2. 実施例１のピストンが吸込み工程の下死点近傍位置におけるシリンダボア切欠き部の位置と油膜の関係を示した要部断面模式図。FIG. 4 is a schematic cross-sectional view of a main part showing a relationship between a position of a cylinder bore cutout portion and an oil film at a position near a bottom dead center of a piston in a suction process in the first embodiment. 比較例として下切欠き部を有さないピストンが圧縮工程の下死点近傍位置にあるときの要部断面図Sectional view of a main part when a piston without a lower notch is located at a position near the bottom dead center of the compression process as a comparative example 図５のA'-A'断面について圧縮時にピストンにかかる油膜反力を表した模式図FIG. 5 is a schematic diagram showing the oil film reaction force applied to the piston during compression with respect to section A′-A ′ in FIG.

以下、本発明の実施例を、添付の図面を参照しつつ説明する。本実施例における下方向は、重力加速度の方向と同一にしても良いしそれ以外の方向と同一にしても良い。   Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings. The downward direction in this embodiment may be the same as the direction of the gravitational acceleration, or may be the same as the other directions.

図１は実施例１の密閉型電動圧縮機の縦断面図である。密閉容器１内に設けられたシリンダブロック２は軸受部２ａとシリンダボア２ｂを一体で形成しており、シリンダボア２ｂ内をピストン３が往復動して圧縮要素を構成する。シリンダボア２ｂはピストン３が摺動する円筒状の空隙を有しており、ピストン３は略円柱状である。   FIG. 1 is a vertical sectional view of the hermetic electric compressor of the first embodiment. The cylinder block 2 provided in the sealed container 1 integrally forms a bearing 2a and a cylinder bore 2b, and a piston 3 reciprocates in the cylinder bore 2b to form a compression element. The cylinder bore 2b has a cylindrical space in which the piston 3 slides, and the piston 3 is substantially cylindrical.

シリンダブロック２に固定されたステータ４及び電動機に連結するロータ５によって電動要素を構成し、ロータ５に固定されたクランクシャフト７を回転させることで圧縮要素に動力を伝える。クランクシャフト７は回転中心から偏心した位置にクランクピン７ａを有し、クランクピン７ａとピストン３との間はコンロッド８及びピストンピン９によって回転自在に連結され、クランクシャフト７の回転運動をピストン３の往復運動へと変換する。   An electric element is constituted by the stator 4 fixed to the cylinder block 2 and the rotor 5 connected to the electric motor, and power is transmitted to the compression element by rotating a crankshaft 7 fixed to the rotor 5. The crankshaft 7 has a crankpin 7a at a position eccentric from the center of rotation. The crankpin 7a and the piston 3 are rotatably connected by a connecting rod 8 and a piston pin 9, and the rotational movement of the crankshaft 7 is controlled by the piston 3 To reciprocating motion.

シリンダボア２ｂ上部に設けた上面視略Ｕ字形状の上切欠き部２ｃはシリンダブロック２上壁まで貫通しており、組立て時に予めシリンダボア２ｂ内に挿入したピストン３とクランクピン７ａに挿入したコンロッド８を上切欠き部２ｃからピストンピン９を挿入することで各部品を組み立てるものである。   The upper notch 2c, which is substantially U-shaped when viewed from above and is provided above the cylinder bore 2b, penetrates to the upper wall of the cylinder block 2, and the piston 3 previously inserted into the cylinder bore 2b and the connecting rod 8 inserted into the crank pin 7a during assembly. Are assembled by inserting the piston pin 9 from the upper notch 2c.

なお、クランクシャフト７は内部に給油通路を有し、回転による遠心力を利用して密閉容器１内に貯留した潤滑油を上方へと吸い上げ、クランクピン７ａ上部の噴出口及びコンロッド８内に同じく形成された給油通路から圧縮要素へと潤滑油を供給する。   The crankshaft 7 has an oil supply passage therein, and uses the centrifugal force of rotation to suck up the lubricating oil stored in the sealed container 1 upward, and similarly to the spout and the connecting rod 8 above the crankpin 7a. The lubricating oil is supplied from the formed oil supply passage to the compression element.

シリンダボア２ｂの先端は、冷媒の吸込み口及び吐出口とそれぞれの経路口の冷媒流れを調節するバルブを有する、バルブプレート６によって封止されており、ピストン３とシリンダボア２ｂとの間は潤滑油によってシールされ、冷媒吸込み時及び圧縮時に冷媒はバルブプレート６の冷媒経路口を通して流れる。   The tip of the cylinder bore 2b is sealed by a valve plate 6, which has a suction port and a discharge port for the refrigerant and a valve for adjusting the flow of the refrigerant in each of the passage ports, and the space between the piston 3 and the cylinder bore 2b is lubricated. It is sealed, and the refrigerant flows through the refrigerant passage opening of the valve plate 6 when the refrigerant is sucked and compressed.

低速回転時には、回転による遠心力が小さくなるため、クランクシャフト７による潤滑油の吸い上げ量が小さくなり、圧縮要素に供給される潤滑油の量が減少し、ピストン３とシリンダボア２ｂとの間のシール性が低下することで、圧縮時に冷媒が漏れやすくなる。このため、シール性の改善が望まれる。   During low-speed rotation, the centrifugal force due to the rotation is reduced, so that the amount of lubricating oil sucked up by the crankshaft 7 is reduced, the amount of lubricating oil supplied to the compression element is reduced, and the seal between the piston 3 and the cylinder bore 2b is reduced. The deterioration of the property makes it easier for the refrigerant to leak during compression. For this reason, improvement in the sealing performance is desired.

図２は本実施例のピストン３が圧縮工程の下死点近傍位置にあるときの要部断面図である。図３は図２のA-A断面視で、圧縮時にピストン３にかかる油膜反力を表した模式図である。
ピストン３外周には環状の給油溝３１が１つ以上ピストン３の軸方向（往復動方向）に並んで凹設されている。給油溝３１は、ピストン３の回転中心位置、本実施例ではピストンピン９位置に対して、軸方向で別の位置に設けられている。本実施例では、回転中心位置よりも上死点側の位置に設けられている。
シリンダボア２ｂには、ピストン３が往復動する円筒状の空隙が設けられている。シリンダボア２ｂは、軸方向視で、空隙の中心を挟んで対向する２つの切欠き部２ｃ，２ｄを有している。切欠き部２ｃ，２ｄは、シリンダボア２ｂの上側及び下側に位置すると、上側の切欠き部２ｃを通してピストンピン９を挿入しやすく、また、噴出口から供給される潤滑油が届きやすいため好ましい。 FIG. 2 is a cross-sectional view of a main part when the piston 3 of the present embodiment is located near the bottom dead center of the compression process. FIG. 3 is a schematic diagram showing an oil film reaction force applied to the piston 3 during compression in a cross-sectional view taken along the line AA of FIG.
One or more annular oil supply grooves 31 are formed in the outer periphery of the piston 3 so as to be arranged in the axial direction (reciprocating direction) of the piston 3. The oil supply groove 31 is provided at another position in the axial direction with respect to the rotation center position of the piston 3, in this embodiment, the position of the piston pin 9. In this embodiment, it is provided at a position closer to the top dead center than the rotation center position.
The cylinder bore 2b is provided with a cylindrical space in which the piston 3 reciprocates. The cylinder bore 2b has two notches 2c and 2d facing each other across the center of the gap when viewed in the axial direction. The notches 2c and 2d are preferably located above and below the cylinder bore 2b, because the piston pin 9 can be easily inserted through the upper notch 2c and the lubricating oil supplied from the jet port can easily reach.

ピストン３が最もシリンダボア２ｂから引き出される下死点において、給油溝３１の上部は、シリンダボア２ｂの上切欠き部２ｃを介して露出している。また、給油溝３１の下部は、シリンダボア２ｂの下切欠き部２ｄを介して露出している。   At the bottom dead center where the piston 3 is most pulled out from the cylinder bore 2b, the upper part of the oil supply groove 31 is exposed through the upper cutout 2c of the cylinder bore 2b. The lower part of the oil supply groove 31 is exposed through the lower notch 2d of the cylinder bore 2b.

クランクピン７ａ上部から噴出された潤滑油が上切欠き部２ｃを通して給油溝３１の上部にかかり、給油溝３１全周へと伝わって供給される。さらに、圧縮時にピストン３がシリンダボア２ｂへと押し込まれていくと、給油溝３１はシリンダボア２ｂ内に完全に入り、シリンダボア２ｂ内壁と給油溝３１によって潤滑油が保持されることで、低速回転時の小さい潤滑油供給量においても、ピストン３とシリンダボア２ｂとの間のシール性を高く維持することができる。   The lubricating oil ejected from the upper part of the crank pin 7a is applied to the upper part of the oil supply groove 31 through the upper notch 2c, and is transmitted and supplied to the entire circumference of the oil supply groove 31. Further, when the piston 3 is pushed into the cylinder bore 2b at the time of compression, the oil supply groove 31 completely enters the cylinder bore 2b, and the lubricating oil is held by the inner wall of the cylinder bore 2b and the oil supply groove 31, so that the lubrication oil at the time of low-speed rotation is obtained. Even with a small amount of lubricating oil supplied, the sealing performance between the piston 3 and the cylinder bore 2b can be kept high.

給油溝３１に供給された潤滑油は、ピストン３とシリンダボア２ｂとの隙間に油膜を形成し、油膜によって圧縮冷媒の圧力を受けることで低圧側への冷媒漏れを抑える働きをする。つまり、圧縮時には油膜は圧縮冷媒から圧力を受け、これは油膜反力としてピストン３にも伝わる。   The lubricating oil supplied to the oil supply groove 31 forms an oil film in the gap between the piston 3 and the cylinder bore 2b, and acts to suppress refrigerant leakage to the low pressure side by receiving the pressure of the compressed refrigerant by the oil film. In other words, during compression, the oil film receives pressure from the compressed refrigerant, which is transmitted to the piston 3 as an oil film reaction force.

下死点において給油溝３１の一部は、上切欠き部２ｃ又は下切欠き部２ｄを介してシリンダボア２ｂから露出する。給油溝３１を複数設ける場合、全ての給油溝３１に潤滑油を供給するために、下死点において、全ての給油溝３１の上部がシリンダボア２ｂから露出することが好ましい。即ち、最も上死点側に近い給油溝３１ａのうち、下死点側の溝端部３２ｂ上部が下死点において上切欠き部２ｃ及び下切欠き部２ｄそれぞれから露出することが好ましい。反力は、給油溝３１ａに溜められた潤滑油がシリンダボア２ｂとピストン３との間に挟まれることで生じるから、圧縮工程では主に、給油溝３１のうち移動方向後端（すなわち、下死点側の端部３２ｂ）に存在する潤滑油によって生じる。   At the bottom dead center, a part of the oil supply groove 31 is exposed from the cylinder bore 2b via the upper notch 2c or the lower notch 2d. When a plurality of oil supply grooves 31 are provided, it is preferable that the upper portions of all the oil supply grooves 31 be exposed from the cylinder bores 2b at the bottom dead center in order to supply the lubricant oil to all the oil supply grooves 31. That is, of the oil supply groove 31a closest to the top dead center side, it is preferable that the upper part of the groove end 32b on the bottom dead center side is exposed from the upper notch 2c and the lower notch 2d at the bottom dead center. Since the reaction force is generated when the lubricating oil stored in the oil supply groove 31a is caught between the cylinder bore 2b and the piston 3, the compression process mainly includes the rear end of the oil supply groove 31 in the moving direction (ie, bottom dead end). It is caused by the lubricating oil present at the point 32b).

本実施例では、ピストン３の軸方向視について、シリンダボア２ｂの中心周りで、上切欠き部２ｃに略点対称な位置に下切欠き部２ｄが設けられている。このため、下死点近傍の圧縮工程において給油溝３１に貯留した潤滑油がピストン３とシリンダボア２ｂの間に形成する油膜１０及びその油膜反力がピストン３の軸中心に対して略対称となり、ピストン３に働く転覆モーメント（ピストン３の径方向視で、ピストン重心周りに回転するモーメント）を抑えることができる。なお、ピストン３の三次元構造としては、例えば面対称にすることができる。   In this embodiment, a lower notch 2d is provided at a position substantially point-symmetric to the upper notch 2c around the center of the cylinder bore 2b when viewed in the axial direction of the piston 3. Therefore, the oil film 10 formed between the piston 3 and the cylinder bore 2b by the lubricating oil stored in the oil supply groove 31 in the compression step near the bottom dead center and the oil film reaction force are substantially symmetric with respect to the axial center of the piston 3, The overturning moment acting on the piston 3 (the moment rotating around the center of gravity of the piston 3 in the radial direction of the piston 3) can be suppressed. The three-dimensional structure of the piston 3 can be, for example, plane-symmetric.

上切欠き部２ｃと下切欠き部２ｄはそれぞれ、ピストン３の軸方向位置で略同一の位置に存在することができる。すなわち、上切欠き部２ｃを介して露出する給油溝３１の長さと下切欠き部２ｄを介して露出する給油溝３１の長さとは、略同一であることができる。
具体的には、上切欠き部２ｃの内周側端部とシリンダボア２ｂの軸方向視の中心とをそれぞれ通る２本の仮想の直線を考えると、これら２本の直線に挟まれた領域に、下切欠き部２ｄが存在する。下切欠き部２ｄは、この領域内の全域に亘り、領域外には存在しないことが最も好ましいが、この領域の一部のみに実質的に存在する場合でも効果を奏する。 The upper notch 2c and the lower notch 2d can be located at substantially the same axial position of the piston 3. That is, the length of the oil supply groove 31 exposed through the upper notch 2c and the length of the oil supply groove 31 exposed through the lower notch 2d can be substantially the same.
Specifically, considering two virtual straight lines that respectively pass through the inner peripheral end of the upper notch portion 2c and the center of the cylinder bore 2b when viewed in the axial direction, the region between the two straight lines is , The lower notch 2d exists. It is most preferable that the lower notch portion 2d does not exist outside the entire region in the region, but the effect is obtained even when the lower notch portion 2d substantially exists only in a part of the region.

加工性の観点から、下切欠き部２ｄの位置は上切欠き部２ｃに対して完全には対称にならないことが考えられる。上切欠き部２ｃと下切欠き部２ｄの軸方向位置に差があると、圧縮工程が進んだ際に給油溝３１に貯留した潤滑油がピストン３とシリンダボア２ｂの間に形成する油膜１０及びその油膜反力が上下非対称となる瞬間が生じ得る。しかし、少なくとも、下死点において給油溝３１下部が下切欠き部２ｄから露出する位置関係とすることによって、下切欠き部２ｄから露出する部分の給油溝３１に貯留した潤滑油は給油溝３１から流出し、再度上切欠き部２ｃから供給される潤滑油によって給油溝３１が満たされるまで、油膜反力の上下非対称性による転覆モーメントを抑えることができる。   From the viewpoint of workability, the position of the lower notch 2d may not be completely symmetrical with respect to the upper notch 2c. If there is a difference in the axial position between the upper notch portion 2c and the lower notch portion 2d, the lubricating oil stored in the oil supply groove 31 when the compression process proceeds proceeds, and the oil film 10 formed between the piston 3 and the cylinder bore 2b and the oil film 10 There may occur a moment when the oil film reaction force becomes vertically asymmetric. However, at least at the bottom dead center, the lower part of the oil supply groove 31 is exposed from the lower notch 2d so that the lubricating oil stored in the oil supply groove 31 at the portion exposed from the lower notch 2d flows out of the oil supply groove 31. However, the overturning moment due to the vertical asymmetry of the oil film reaction force can be suppressed until the oil supply groove 31 is filled with the lubricating oil supplied from the upper notch 2c again.

また、ピストン３とシリンダボア２ｂとの間のシール性は圧縮時だけでなく、吸込み時についても必要とされる。吸込み時のシール性を高めることで、適切な経路で冷媒を流すことにより冷媒の流体音を抑制できるほか、冷媒ガスの密度を高くすることができ、性能向上につながる。また、吸込み時にシールが不十分であると、漏れた冷媒と共に潤滑油がシリンダボア２ｂ内に入り込み、圧縮吐出される冷媒の中に潤滑油が混ざり込み、冷凍サイクルの冷力を低下させる要因となる。   Further, the sealing performance between the piston 3 and the cylinder bore 2b is required not only at the time of compression but also at the time of suction. By improving the sealing performance at the time of suction, by flowing the refrigerant through an appropriate path, the fluid noise of the refrigerant can be suppressed, and the density of the refrigerant gas can be increased, leading to an improvement in performance. Further, if the seal is insufficient at the time of suction, the lubricating oil enters the cylinder bore 2b together with the leaked refrigerant, and the lubricating oil mixes with the refrigerant to be compressed and discharged, which causes a reduction in the cooling power of the refrigeration cycle. .

図４は、本実施例の吸込み工程の下死点近傍におけるシリンダボア２ｂ切欠き部の位置と油膜１０の関係を示した要部断面図である。吸込み時はピストン３が下死点側へと動くため、給油溝３１のうち、上死点側の端部３２がシリンダボア２ｂから露出していれば反力が生じず、シリンダボア２ｂ内に位置すれば反力が生じ得る。   FIG. 4 is a cross-sectional view of a main part showing the relationship between the position of the notched portion of the cylinder bore 2b and the oil film 10 near the bottom dead center of the suction step of the present embodiment. At the time of suction, the piston 3 moves to the bottom dead center side. Therefore, if the end 32 of the oil supply groove 31 on the top dead center side is exposed from the cylinder bore 2b, no reaction force occurs, and the piston 3 is located in the cylinder bore 2b. If a reaction force is generated.

本実施例では、図４に示すように、最も上死点側に近い給油溝３１ａのうち、上死点側の端部３２ａが、下死点においても上切欠き部２ｃ及び下切欠き部２ｄから露出しないように設定している。このような位置関係とすることにより、吸込み工程において常に給油溝３１ａに貯留した潤滑油がピストン３とシリンダボア２ｂの間に油膜を形成し、シール性を維持することができる。   In the present embodiment, as shown in FIG. 4, the end 32a on the top dead center side of the oil supply groove 31a closest to the top dead center side has the upper notch 2c and the lower notch 2d even at the bottom dead center. It is set not to be exposed from. With such a positional relationship, the lubricating oil stored in the oil supply groove 31a always forms an oil film between the piston 3 and the cylinder bore 2b in the suction process, and the sealing property can be maintained.

上切欠き部２ｃにおける給油溝３１ａの露出量は給油溝３１ａへの潤滑油の供給量に影響するため、潤滑油の供給量を確保することを優先した場合、端部３２ａは上切欠き部２ｃから露出するように設定することも考えられるし、例えば給油溝３１ａの軸方向寸法を長く設けることで、端部３２ａはシリンダボア２ｂ内に位置するようにしつつそれ以外の給油溝３１ａの部分が露出するようにすることも考えられる。   Since the exposed amount of the oil supply groove 31a in the upper notch portion 2c affects the supply amount of the lubricating oil to the oil supply groove 31a, if the priority is given to ensuring the supply amount of the lubricating oil, the end portion 32a has the upper notch portion. It is also conceivable to set the oil supply groove 31a so as to be exposed. For example, by providing the oil supply groove 31a with a long axial dimension, the other end of the oil supply groove 31a is positioned inside the cylinder bore 2b while the oil supply groove 31a is located in the cylinder bore 2b. It is also conceivable to expose it.

一方で、給油溝３１に貯留する潤滑油は溝３１を伝って下方へと流れるため、下切欠き部２ｄについては、油膜によるシールを維持できずに冷媒が漏れたとき、冷媒と共にシリンダボア２ｂ内に漏れ入ってしまう潤滑油の量も多くなるため、端部３２ａを下切欠き部２ｄから出ないようにすることは、吐出冷媒に混ざり込む潤滑油の量を抑える効果が大きい。   On the other hand, since the lubricating oil stored in the oil supply groove 31 flows downward along the groove 31, the lower notch 2d cannot be maintained in the oil film seal, and when the refrigerant leaks, it enters the cylinder bore 2b together with the refrigerant. Since the amount of lubricating oil that leaks in increases, preventing the end 32a from coming out of the lower notch 2d has a large effect of suppressing the amount of lubricating oil mixed into the discharged refrigerant.

比較例Comparative example

図５は比較例として下切欠き部２ｄを有さないピストン３が圧縮工程の下死点近傍位置にあるときの要部断面図であり、図６は図５のA'-A'断面について圧縮時にピストン３にかかる油膜反力を表した模式図である。   FIG. 5 is a cross-sectional view of a relevant part when the piston 3 having no lower notch 2d is located at a position near the bottom dead center in the compression step as a comparative example, and FIG. FIG. 3 is a schematic diagram showing an oil film reaction force sometimes applied to a piston 3.

比較例の場合、下死点近傍の圧縮工程においては、上切欠き部２ｃ側で給油溝３１がシリンダボア２ｂから露出しているのみのため、油膜１０は、上切欠き部２ｃを除く全周に形成される。   In the case of the comparative example, in the compression step near the bottom dead center, since the oil supply groove 31 is only exposed from the cylinder bore 2b on the side of the upper notch 2c, the oil film 10 has the entire circumference excluding the upper notch 2c. Formed.

すると、ピストン３にかかる油膜反力は図６のように非対称に発生するため、油膜反力の合成力はピストン３を径方向視で回転するように働き、ピストン３の軸に対して回転させる転覆モーメントがかかる。   Then, since the oil film reaction force applied to the piston 3 is generated asymmetrically as shown in FIG. 6, the resultant force of the oil film reaction force acts to rotate the piston 3 in a radial direction and rotates the piston 3 with respect to the axis of the piston 3. An overturning moment is applied.

油膜反力及び転覆モーメントは高速回転時ほど大きくなるため、圧縮機の製品仕様として高い最高回転数を持つ場合に、より大きな問題となる。   Since the oil film reaction force and the overturning moment increase as the rotation speed increases, the problem becomes more serious when the compressor has a high maximum rotation speed as a product specification.

１ 密閉容器
２ シリンダブロック
２ａ 軸受部
２ｂ シリンダボア
２ｃ 上切欠き部（第１切欠き部）
２ｄ 下切欠き部（第２切欠き部）
３ ピストン
４ ステータ
５ ロータ
６ バルブプレート
７ クランクシャフト
７ａ クランクピン
８ コンロッド
９ ピストンピン
１０ 油膜
３１ 給油溝
３１ａ 最も上死点に近い給油溝
３２ａ 最も上死点に近い給油溝のうち上死点側の端部
３２ｂ 最も上死点に近い給油溝のうち下死点側の端部 DESCRIPTION OF SYMBOLS 1 Closed container 2 Cylinder block 2a Bearing part 2b Cylinder bore 2c Upper notch (first notch)
2d Lower notch (2nd notch)
Reference Signs List 3 piston 4 stator 5 rotor 6 valve plate 7 crankshaft 7a crankpin 8 connecting rod 9 piston pin 10 oil film 31 oil supply groove 31a oil supply groove closest to top dead center 32a oil supply groove closest to top dead center End 32b The end of the lubrication groove closest to the top dead center on the bottom dead center side

Claims (6)

円筒状の空隙が設けられたシリンダボアを有するシリンダと、
該空隙内を往復動するピストンと、を備え、
前記シリンダボアと前記ピストンとの間に潤滑油が供給される圧縮機であって、
前記シリンダボアは、前記空隙を挟んで互いに対向する第１切欠き部及び第２切欠き部を有することを特徴とする圧縮機。 A cylinder having a cylinder bore provided with a cylindrical gap,
A piston reciprocating in the gap,
A compressor in which lubricating oil is supplied between the cylinder bore and the piston,
The compressor according to claim 1, wherein the cylinder bore has a first notch and a second notch facing each other with the gap interposed therebetween. 前記第１切欠き部と前記第２切欠き部の何れか一方は、前記空隙に対して重力加速度の方向と逆側に位置することを特徴とする請求項１に記載の圧縮機。   2. The compressor according to claim 1, wherein one of the first notch and the second notch is located on a side opposite to a direction of a gravitational acceleration with respect to the gap. 3. 前記ピストンは、円環状の給油溝を有し、
前記ピストンの下死点において、該給油溝は、
前記第１切欠き部を介して前記シリンダボアから露出する部分と、
前記第２切欠き部を介して前記シリンダボアから露出する部分と、
前記シリンダボアに対向する部分と、を有することを特徴とする請求項１又は２に記載の圧縮機。 The piston has an annular oil supply groove,
At the bottom dead center of the piston, the oil groove is:
A portion exposed from the cylinder bore through the first notch;
A portion exposed from the cylinder bore through the second notch;
The compressor according to claim 1, further comprising: a portion facing the cylinder bore. 前記給油溝のうち、
周方向で前記第１切欠き部側に位置する部分の上死点側の端部は、前記ピストンの下死点において、前記第１切欠き部より上死点側に位置し、及び／又は、
周方向で前記第２切欠き部側に位置する部分の上死点側の端部は、前記ピストンの下死点において、前記第２切欠き部より上死点側に位置することを特徴とする請求項３に記載の圧縮機。 Of the lubrication groove,
An end on the top dead center side of a portion located on the first notch side in the circumferential direction is located on the top dead center side of the first notch at the bottom dead center of the piston, and / or ,
An end at a top dead center side of a portion located on the side of the second notch in the circumferential direction is located at a top dead center side of the second notch at a bottom dead center of the piston. The compressor according to claim 3, wherein 前記ピストンの往復動方向における断面視において、前記第１切欠き部の端部と前記空隙の中心それぞれを略通過する２本の仮想の直線で挟まれる領域に、前記第２切欠き部の一部が収まることを特徴とする請求項１乃至４何れか一項に記載の圧縮機。   In a cross-sectional view in the reciprocating direction of the piston, the area of the second notch is defined by an area between two virtual straight lines that substantially pass through the end of the first notch and the center of the gap. The compressor according to any one of claims 1 to 4, wherein the section is accommodated. 前記ピストンの往復動方向における断面視において、前記第１切欠き部の端部と前記空隙の中心それぞれを略通過する２本の仮想の直線で挟まれる領域に、前記第２切欠き部の全部が収まることを特徴とする請求項１乃至４何れか一項に記載の圧縮機。   In a cross-sectional view in the reciprocating direction of the piston, the entire area of the second notch is sandwiched by two virtual straight lines that substantially pass through the end of the first notch and the center of the gap. The compressor according to any one of claims 1 to 4, wherein?
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