JPH02146287A - Rotary type compressor - Google Patents

Abstract

PURPOSE:To reduce frictional loss between a shaft and a bearing by providing a bearing member having a recessed part with an area less than one eighth of the whole inner surface and with a fixed depth in a main and a sub bearings at the circumferential angel of less than 90 deg. from a vane in the reversely rotating direction of the shaft. CONSTITUTION:The recessed part 18a provided on the inner diameter side of a bearing member 18 fitted into a main bearing 7 is positioned within at least 90 deg. from the position of a vane 6 in the reversely rotating direction of a shaft 3, and its area is made less than one eighth of the whole inner surface area. With this structure, the shaft 3 is eccentric approximately in the range of 120 deg.theta1-180 deg.theta2 due to the load acted upon the shaft 3 at the time of operation, so that frictional loss generated by the friction between the fluid and lubricating oil supplied between the shaft 3 and the bearing member 18 is decreased by providing the recessed part 18a at the bearing member 18 on the reverse eccentricity side of the shaft 3. In addition fluid friction is scarcely generated by making the depth of the recessed part 18a 0.1-0.5mm, so that frictional loss can be reduced.

Description

【発明の詳細な説明】 産業上の利用分野 本発明は、冷凍サイクル等に使用する回転式圧縮機に関
し、特に摺動損失の少ない構成に係わる。DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a rotary compressor used in a refrigeration cycle or the like, and particularly relates to a configuration with little sliding loss.

従来の技術 従来の構成を第６図、第７図を用いて説明する。Conventional technology The conventional configuration will be explained using FIGS. 6 and 7.

１は密閉ケーシング、２は電動機部であり、シャフト３
を介してシリンダ４、ローラ６、ベーン６、主軸受子、
副軸受８により構成される機械部本体９と連結している
。シャフト３は主軸３ａ、副軸３ｂ、クランク３Ｃより
なる。１ｏはベーン背面に設けられたスプリングである
。１１ａ、１１ｂはシリンダ４内で、ローラ６、ベーン
６、主軸受７、副軸受８により構成される吸入室と圧縮
室である。１２はシャフト３と連結する給油機構である
。１３は副軸受８に固定された吸入管であり、吸入通路
１４を介して吸入室１１ａと連通している。１６は吐出
孔であり吐出弁（図示せず）を介して密閉ケーシング１
内と連通している。１６は吐出管であり密閉ケーシング
１内に開放している。1 is a sealed casing, 2 is an electric motor section, and shaft 3
Through the cylinder 4, roller 6, vane 6, main bearing,
It is connected to a mechanical part main body 9 constituted by a sub-bearing 8. The shaft 3 consists of a main shaft 3a, a sub-shaft 3b, and a crank 3C. 1o is a spring provided on the back side of the vane. Reference numerals 11a and 11b are a suction chamber and a compression chamber in the cylinder 4, which are constituted by a roller 6, a vane 6, a main bearing 7, and a sub-bearing 8. 12 is an oil supply mechanism connected to the shaft 3. Reference numeral 13 denotes a suction pipe fixed to the sub-bearing 8, and communicates with the suction chamber 11a via a suction passage 14. Reference numeral 16 denotes a discharge hole, which is connected to the sealed casing 1 through a discharge valve (not shown).
It communicates with the inside. Reference numeral 16 denotes a discharge pipe that opens into the sealed casing 1.

１７は冷媒が一部溶は込んだ潤滑油である。17 is a lubricating oil into which refrigerant is partially dissolved.

次に回転式圧縮機の圧縮機構について説明する。Next, the compression mechanism of the rotary compressor will be explained.

冷却システム（図示せず）から冷媒ガスは、吸入管１３
、吸入通路１４ａ、１４ｂより導かれシリンダ４内の吸
入室１１ａに至る。吸入室１１ａに至った冷媒ガスは、
シャフト３のクランク３Ｃに回転自在に収納されたロー
ラ６とベーン６により仕切られた圧縮［１１ｂで、電動
機部２の回転に伴うシャフト３０回転運動により漸次圧
縮される。Refrigerant gas from the cooling system (not shown) is supplied to the suction pipe 13
, are guided through the suction passages 14a and 14b and reach the suction chamber 11a inside the cylinder 4. The refrigerant gas that has reached the suction chamber 11a is
Compression [11b] partitioned by rollers 6 and vanes 6 rotatably housed in the crank 3C of the shaft 3 is gradually compressed by rotational movement of the shaft 30 as the electric motor section 2 rotates.

圧縮された冷媒ガスは、吐出孔１６、吐出弁を介して密
閉ケーシング１内に一旦吐出された後、吐出管１６を介
し冷却システムに吐出される。The compressed refrigerant gas is once discharged into the sealed casing 1 through the discharge hole 16 and the discharge valve, and then discharged to the cooling system through the discharge pipe 16.

次に冷媒が一部溶は込んだ潤滑油１７の流れについて説
明する。潤滑油１７は給油機溝分介して、シャフト３と
主軸受７、副軸受８、ローラ６間の摺動部に送られた後
、一部は直接密閉ケーシング１下部に戻り一部は圧縮室
１１ｂに入り、冷媒ガスと共に吐出され密閉ケーシング
１の下部に戻る。Next, the flow of the lubricating oil 17 in which the refrigerant is partially dissolved will be explained. After the lubricating oil 17 is sent to the sliding parts between the shaft 3, the main bearing 7, the sub-bearing 8, and the rollers 6 through the feeder groove, part of it returns directly to the lower part of the sealed casing 1 and part of it goes into the compression chamber. 11b, is discharged together with the refrigerant gas, and returns to the lower part of the sealed casing 1.

次に主軸受７、副軸受８の構成について説明する。Next, the configurations of the main bearing 7 and the sub-bearing 8 will be explained.

いずれの軸受とも、真円軸受であり、一般的にシャフト
３の直径の約１／１０００の隙間を有する。Both bearings are perfectly circular bearings, and generally have a gap of about 1/1000 of the diameter of the shaft 3.

従ってシャフト３にガス圧荷重などの種々の荷重が作用
して主軸受７、副軸受８に対してシャフト３が偏心し前
記隙間がより狭くなった時には、くさび効果による油膜
圧力が発生し、シャフト３の偏心は最小限にとどまる。Therefore, when various loads such as gas pressure loads act on the shaft 3 and the shaft 3 becomes eccentric with respect to the main bearing 7 and the sub-bearing 8 and the gap becomes narrower, an oil film pressure is generated due to the wedge effect, and the shaft 3 eccentricity remains minimal.

よって耐荷重性が向上、信頼性が向上するとの効果があ
った。Therefore, there was an effect that the load resistance was improved and the reliability was improved.

発明が解決しようとする課題 この様な構成では、シャフトが主軸受、副軸受に対して
偏心して、両者間の隙間のうち一方が狭く、他方が広く
なっても、もともとの隙間が狭いためにシャフトが回転
する際にはシャフトと両軸受との隙間に供給されている
潤滑油との間で円周全域にわたって流体摩擦が発生し、
摩擦損失の増大による圧縮機の効率が低下するといった
問題があった。尚、軸受には潤滑油の供給のため、／Ｉ
′ｌｌ溝を設ける場合があるが、油ｕ４の巾が狭く流体
摩擦を大巾に低減するには至らなかった。Problems to be Solved by the Invention In such a configuration, even if the shaft is eccentric with respect to the main bearing and the sub-bearing, and one of the gaps between them becomes narrow and the other wide, the original gap becomes narrower. When the shaft rotates, fluid friction occurs over the entire circumference between the shaft and the lubricating oil supplied to the gap between the bearings.
There was a problem in that the efficiency of the compressor decreased due to increased friction loss. Additionally, in order to supply lubricating oil to the bearing, /I
In some cases, a groove is provided, but the width of the oil u4 is narrow and it has not been possible to significantly reduce fluid friction.

本発明は上記従来例の欠点を解消するものであり、軸受
を全周３６０°のうち一部に凹部を有する部材で構成す
ることにより、耐荷重性、信頼性を低下させることなく
シャフトと軸受間の摩擦損失を低減することを目的とし
ている。The present invention eliminates the drawbacks of the conventional example described above, and by constructing the bearing with a member having a concave portion in a part of the entire 360° circumference, the shaft and the bearing can be easily connected without deteriorating the load resistance and reliability. The purpose is to reduce friction loss between

課題を解決するための手段 本発明は、主軸受、副軸受の少なくともいずれかの軸受
内に、その円周方向角度でベーンからシャフトの父回転
方向へ少くとも９０°内に全内表面積のｉ以下の面積の
四部を有する部材を備えたものである。Means for Solving the Problems The present invention provides that the total internal surface area i of the main bearing or the sub bearing is within at least 90° from the vane to the main rotational direction of the shaft in the circumferential direction of the bearing. It is equipped with a member having four parts with the following areas.

作　　　用 本発明は上記した構成により、シャフトが回転する際に
シャフトと軸受との間に供給されている潤滑油との流体
摩擦の発生する領域が減少し、軸受の耐荷重性、信頼性
を低下させることなく、シャフトと軸受間の摩擦損失低
減、圧縮機の効率向上が図れる。Effects The present invention has the above-described configuration, which reduces the area where fluid friction occurs between the shaft and the bearing and the lubricating oil supplied between the shaft and the bearing, thereby improving the load bearing capacity and reliability of the bearing. It is possible to reduce friction loss between the shaft and bearings and improve the efficiency of the compressor without any deterioration.

実施例 以下本発明の一実施例を第１図から第３図にて説明する
。尚、従来例と同一部分は同一符号を付し詳細な説明を
省略する。EXAMPLE An example of the present invention will be described below with reference to FIGS. 1 to 3. Note that the same parts as in the conventional example are given the same reference numerals and detailed explanations are omitted.

１８は主軸受７に嵌合された軸受部材であり、１８ａは
、軸受部材の内径側に設けられた四部である。この凹部
１８ａは、ベーン６位置からシャフト３の１１回転方向
への少なくとも９０°内にあシ、四部１８ａの面積は全
内表面積のμ以下である。18 is a bearing member fitted into the main bearing 7, and 18a are four parts provided on the inner diameter side of the bearing member. The recessed portion 18a is located within at least 90° from the position of the vane 6 in the 11th rotation direction of the shaft 3, and the area of the four portions 18a is less than μ of the total inner surface area.

上記構成において、回転圧縮機の運転時には、シャフト
３に作用する荷重は、ガス圧荷重、ベーン６とローラ５
の接動荷重、ローラ６の遠心力、クランク３Ｃの遠心力
であり、これらを総合した荷重は、運【１間条件によっ
ても多少異なるが、ベーン６を基準に吸入通路１４側へ
の円周角度として、常時およそ１２ｏ０（θ　）〜１８
ｏ０（θ２）の範囲であす る。従ってシャフト３は主軸受７、副軸受８に対して前
記角度に偏心角度を加えた範囲内で常時両ｉＱｂ受７．
８側へ偏心する。また、［ｌ１ｉｔ荷重性を特に要求さ
れる最大荷重には偏心角は、回転数によっで異なるがか
なり小さくなり、はぼシャフト３は１２０°（θ　）〜
１８０°（θ２）の範囲で偏心するため、シャフト３の
反偏心側の軸受部材１８に凹部１８ａを設けることによ
り、シャフト３と軸受部材１８川に供給されている潤滑
油１７との流体摩擦による摩擦損失が低減する。しかし
彦がら凹部１８ａを大きくとりすぎると、軸受部材１８
に対してシャフト３の偏心Ｘが従来以−ヒに大きくなり
、摩擦損失が増大するため、凹部１８ａの領域を円周方
向角＆でベーン６からシャフト３の反回転方向への少な
くとも９ｏ０内に、全内表面積の１／８以下の面積とす
ることによって、従来のシャフト３と同等の偏心となり
、耐荷重性は変わらず特性も変わらない。また凹部１８
ａの深さは０．１〜０．６鴎とすることによって流体摩
擦は殆んど発生せず、摩擦損失は低減する。また、起動
時においては、シャフト３は遠心力によって軸受部材１
８側に寄るが、軸受部材１８の円周方向にわたり四部が
存在しない領域１８ｂを設けることによって、起動時の
耐荷重性も維持することができる。In the above configuration, during operation of the rotary compressor, the load acting on the shaft 3 is the gas pressure load, the vane 6 and the roller 5.
, the centrifugal force of the roller 6, and the centrifugal force of the crank 3C, and the total load of these is the circumferential load on the suction passage 14 side with respect to the vane 6, although it varies somewhat depending on the operating conditions. As an angle, it is always approximately 12o0 (θ ) ~ 18
The range is o0(θ2). Therefore, the shaft 3 is always held within the range of the above angle plus the eccentric angle with respect to the main bearing 7 and the sub bearing 8.
Eccentric to the 8 side. In addition, the eccentric angle for the maximum load that requires particularly high loadability will vary depending on the rotation speed, but the eccentric angle will be quite small, and the shaft 3 will be 120° (θ) ~
Since the shaft 3 is eccentric within a range of 180° (θ2), by providing a recess 18a in the bearing member 18 on the opposite side of the shaft 3, fluid friction between the shaft 3 and the lubricating oil 17 supplied to the bearing member 18 is caused. Friction loss is reduced. However, if the concave portion 18a is made too large, the bearing member 18
In contrast, the eccentricity By setting the area to 1/8 or less of the total inner surface area, the eccentricity is equivalent to that of the conventional shaft 3, and the load resistance remains unchanged and the characteristics do not change. Also, the recess 18
By setting the depth of a to 0.1 to 0.6 mm, almost no fluid friction occurs and friction loss is reduced. Furthermore, during startup, the shaft 3 is moved by the bearing member 1 due to centrifugal force.
Although it is closer to the 8th side, by providing the region 18b in which the four parts do not exist over the circumferential direction of the bearing member 18, the load resistance at the time of startup can also be maintained.

さらにこの凹部１８ａを油溝形状とすることにより油溝
とかねることもできる。また、第４図、第５図は前記軸
受部材１８の四部１８ａの形状を斜めの溝１８ａ１．曲
線状の７ｉ′４１８　ａ　２にしたものであるが、これ
によって第１図の軸受部材１８の凹部１８ａと同じ効果
が得られることは言うまでもない。Furthermore, by making the recess 18a into an oil groove shape, it can also serve as an oil groove. 4 and 5 show that the four parts 18a of the bearing member 18 are shaped like oblique grooves 18a1. It goes without saying that the same effect as the recess 18a of the bearing member 18 shown in FIG. 1 can be obtained by using a curved shape 7i'418a2.

又、本実施例では主軸受７に凹部１８ａを有する軸受部
材１８を備えた場合について述べたが、主軸受７及び副
軸受８又は副軸受８のみに備えても良いことは言うまで
もない。Further, in this embodiment, a case has been described in which the main bearing 7 is provided with the bearing member 18 having the recess 18a, but it goes without saying that the main bearing 7 and the sub-bearing 8 or only the sub-bearing 8 may be provided with the bearing member 18.

発明の効果 以上の説明から明らかな様に本発明は、密閉クランクと
、密閉ケーシング内に収納されたシリンダと、シリンダ
の両端に固定された主軸受および副軸受と、主軸受と副
軸受内に回転自在に収納されクランクを有するシャフト
と、シャフトのクランクに嵌められシリンダ内を偏心回
転するロフと、シリンダの溝内を往復運動しローラと当
接することによりシリンダ内を吸入室と圧縮室に分割す
るベーンと、前記主軸受、副軸受の少くともいずれかの
軸受内に、その円周方向角度で前記ペンからシャフト３
の反回１獣方向への少なくとも９００内に全内表面積の
話以下の面積で深さが０．１〜０．６０の凹部を有する
軸受部材とを備えたものであるから、軸受の耐荷重性、
信頼性を低下させることなく、シャフトと軸受間の流体
摩擦損失を低減し、圧縮機の効率向上を図ることができ
る。Effects of the Invention As is clear from the above description, the present invention includes a sealed crank, a cylinder housed in a sealed casing, a main bearing and a sub bearing fixed to both ends of the cylinder, and a main bearing and a sub bearing fixed to each end of the cylinder. A shaft that is rotatably housed and has a crank, a loaf that is fitted into the crank of the shaft and rotates eccentrically inside the cylinder, and the inside of the cylinder is divided into a suction chamber and a compression chamber by reciprocating in the groove of the cylinder and coming into contact with a roller. a shaft 3 from the pen at an angle in the circumferential direction in at least one of the main bearing and the sub-bearing.
The load bearing capacity of the bearing is sex,
It is possible to reduce fluid friction loss between the shaft and bearing and improve compressor efficiency without reducing reliability.

【図面の簡単な説明】 第１図は本発明の一実施例を示す軸受部材のベーン方向
を基準に吸入室側、圧縮室側への展開図、第２図は本発
明の一実施例を示す回転式圧縮機の縦断面図、第３図は
第２図の１−１′線における矢視図、第４図、第５図は
他の実施例を示す軸受部材の第１図と同じ展開図、第６
図は従来の回転式圧縮機の縦断面図、第７図は第６図の
ｎ−ｎ’線における矢視図である。 １・・・・・・密閉ケーシング、３・・・・・・シャフ
ト、３ｃ・・・・・・クランク、４・・・・・・シリン
ダ、６・・・・・・ローラ、６・・・・・・ベーン、７
・・・・・・主軸受、８・・・・・・副軸受、１８・・
・・・・軸受部材、１８ａ、１８ａ１．１８ａ２・・・
・・・凹部。 代理人の氏名　弁理士　粟　野　重　孝　ほか１名１８
−ｍ−輪　受　都　狩 １８ａ−・−凹　部 第１図 Ｏ＠ 第 図 芭閉グーシック １８酊　−一 粁 め の 凹 邪 第 図 １＆ａｔ−−− 曲 緯 状 の 凹 部 Ｏ＠ １８０＠ ３６ゲ[BRIEF DESCRIPTION OF THE DRAWINGS] Fig. 1 is a developed view of a bearing member showing an embodiment of the present invention toward the suction chamber side and the compression chamber side based on the vane direction, and Fig. 2 shows an embodiment of the present invention. FIG. 3 is a longitudinal cross-sectional view of the rotary compressor shown in FIG. 2, and FIGS. 4 and 5 are the same as FIG. Developed view, No. 6
The figure is a longitudinal sectional view of a conventional rotary compressor, and FIG. 7 is a view taken along line nn' in FIG. 6. 1... Sealed casing, 3... Shaft, 3c... Crank, 4... Cylinder, 6... Roller, 6... ...Bane, 7
...Main bearing, 8...Sub bearing, 18...
...Bearing member, 18a, 18a1.18a2...
...concavity. Name of agent: Patent attorney Shigetaka Awano and 1 other person18
-M-Wheel Uke Miyako 18a--Concave part 1st figure O@ Figure 180

Claims (1)

【特許請求の範囲】[Claims] 密閉ケーシングと、密閉ケーシング内に収納されたシリ
ンダと、前記シリンダの両端に固定された主軸受および
副軸受と、前記主軸受と副軸受内に回転自在に収納され
クランクを有するシャフトと、前記シャフトのクランク
に嵌められ前記シリンダ内に偏心回転するローラと、前
記シリンダの溝内を往復運動し前記ローラと当接するこ
とにより前記シリンダ内を吸入室と圧縮室に分割するベ
ーンと、前記主軸受、副軸受の少くともいずれかの軸受
内に、その円周方向角度で前記ベーンからシャフトの反
回転方向に少なくとも９０°内に、全内表面積の１／８
以下の面積で深さが０．１〜０．６ｍｍの凹部を有する
軸受部材とを備えた回転式圧縮機。A sealed casing, a cylinder housed in the sealed casing, a main bearing and a sub-bearing fixed to both ends of the cylinder, a shaft rotatably housed in the main bearing and sub-bearing and having a crank, and the shaft. a roller that is fitted in the crank and rotates eccentrically within the cylinder; a vane that reciprocates within a groove of the cylinder and comes into contact with the roller to divide the inside of the cylinder into a suction chamber and a compression chamber; the main bearing; 1/8 of the total internal surface area within at least one of the secondary bearings at a circumferential angle thereof from said vane to within at least 90° counter-rotational direction of the shaft;
A rotary compressor comprising: a bearing member having a recess having the following area and a depth of 0.1 to 0.6 mm.